Abstract:
A spring latching connector includes a housing having a bore therethrough, a piston slidably received in said bore, circular groove formed in one of said bore and piston and a circular coil spring disposed in said groove for latching said piston and housing together. The groove is sized and shaped for controlling, in combination with a spring configuration, disconnect and connect forces of the spring latching connection.

Description:
The present application claims priority from provisional patent application Ser. No. 60/476,105 filed Jun. 4, 2003. 
    
    
     The present invention generally relates to connectors and is more directly related to the use of canted coil springs in connecting a piston and a housing for mechanical and electrical connection purposes. 
     The connection may used to hold or latch and disconnect or unlatch. Various types of canted coil springs, such as radial, axial, or turn angle springs may be used depending on the characteristics desired for a particular application. 
     Axial springs may be RF with coils canting clockwise or F with coils canting counterclockwise, and installed or mounted with a front angle in front or in back relative to a direction of piston travel in an insertion movement. The springs can be mounted in various manners in a groove in either the piston or the housing. While the spring is generally mounted in a round piston or a round housing, the canted coil spring is capable of being utilized in non-circular applications such as elliptical, square, rectangular, or lengthwise grooves. 
     Various applications require differing force and force ratios for the initial insertion force, the running force, and the force required to latch and disconnect mating parts. The force, the degree of constraint of the spring, the spring design, the materials used, and the ability of the spring and housing combination to apply a scraping motion to remove oxides that may form on mating parts have been found in accordance with the present invention to determine the electrical performance of the connector. Electrical performance means the resistivity and the resistivity variability of the mated parts. 
     SUMMARY OF THE INVENTION 
     It has been found that the force to connect and the force to disconnect as well as the ratio between the two is determined by the position of the point of contact relative to the end point of the major axis of the spring when the disconnect or unlatch force is applied and the characteristics of the spring and the spring installation or mounting. The maximum force for a given spring occurs when the point of contact is close to the end point of the major axis of the spring. The minimum force for a given spring occurs when the contact point is at the maximum distance from the end point of the major axis, which is the end point of the minor axis of the spring. This invention deals in part with the manner in which the end point is positioned. The material, spring design, and method of installing the spring determine the spring influenced performance characteristics of the invention. 
     Accordingly, a spring latching connector in accordance with the present invention generally includes a housing having a bore therethrough along with a piston slidably received in the bore. 
     A circular groove is formed in one of the bore and the piston and a circular coil spring is disposed in the groove for latching the piston in a housing together. 
     Specifically, in accordance with the present invention a groove is sized and shaped for controlling, in combination with a spring configuration, the disconnect and connect forces of the spring latching connector. 
     The circular coil spring preferably includes coils having a major axis and a minor axis and the circular groove includes a cavity for positioning a point of contact in relation to an end of the coil major axis in order to determine the disconnect and the connect forces. More specifically, the groove cavity positions the point of contact proximate the coil major axis in order to maximize the disconnect forces. Alternatively, the groove cavity may be positioned in order that the point of contact is proximate an end of the minor axis in order to minimize the disconnect force. 
     In addition, the coil height and groove width may be adjusted in accordance with the present invention to control the disconnect and connect forces. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The present invention may be more clearly understood with reference to the following detailed description in conjunction with the appended drawings of which: 
         FIG. 1   a  shows a front view of a canted coil spring with the coils canting counterclockwise as indicated by the arrow; 
         FIG. 1   b  shows and enlarged view of the coils; 
         FIG. 1   c  shows the position of the front and back angle; 
         FIG. 1   d  shows the difference between the lengths of the front angle and the back angle; 
         FIG. 1   e  shows the position of the front and back angles; 
         FIG. 1   f  shows a cross sectional view of a radial spring. 
         FIG. 2   a  shows a radial spring in a flat bottom-housing groove; 
         FIG. 2   b  shows a left side view of the spring; 
         FIG. 2   c  shows a front view of a counterclockwise radial spring with a front angle in the front; 
         FIG. 2   d  shows a cross sectional view of the spring; 
         FIG. 2   e  shows a cross sectional view of the spring mounted in a housing, a reference dot point indicating a position of a front angle of a coil, “the end point of a major axis of the coil” being used to explain the relationship between a point of contact and the end point of the major axis of the coil when determining the unlatching or disconnect force, the dot point showing a position of the front angle of the coil; 
         FIGS. 3   a - 3   e  show a radial spring mounted clockwise in a flat bottom housing groove with the front angle in the back, the spring having coils canting clockwise; 
         FIGS. 4   a - 4   e  show a latching radial spring in a standard latching groove, housing mounted (shown in  FIGS. 4   a  and  4   e ); 
         FIGS. 5   a - 5   e  show a radial spring axially loaded with the grooves offset in a latched position eliminating axial play, with  FIGS. 5   a  and  5   e  showing the spring in an axial load position to eliminate axial play, which enhances conductivity and reduces resistivity variable but increases insertion force; 
         FIGS. 6   a - 6   e  and  7   a - 7   e  show the same type of design but piston mounted.  FIGS. 6   a - 6   e  show a latching radial spring in a latching groove, piston mounted, while  FIGS. 7   a - 7   e  shows a latching radial spring with offset axial grooves for minimal axial play piston mounted. The features are the same as indicated in  FIGS. 4   a - 4   e  and  5   a - 5   e  except piston mounted; 
         FIGS. 8   a - 8   d  show a series of circular holding multiple radial spring mounted one in each groove. Each spring is separate from the others,  FIGS. 8   a  and  8   b  showing springs being compressed radially by the shaft as it moves in the direction of the arrow,  FIG. 8   c  showing a cross section of the spring and  FIG. 8   d  showing an enlarged view of a portion of  FIG. 8   a . Springs in a multiple manner could also be axial; 
         FIGS. 9   a - 9   d  show a holding multiple radial springs mounted in multiple grooves, this design being similar to the one indicated in  FIGS. 8   a - 8   d  but the grooves are physically separated from each other, springs in a multiple manner may also be axial; 
         FIGS. 10   a - 10   d  show a holding length spring mounted axially in a threaded groove,  FIG. 10   b  showing the piston partially engaging the housing by deflecting the spring coils,  FIG. 10   a  showing the shaft moving in the direction of the arrow with further compression of the spring coils,  FIG. 10   c  showing a length of the spring and  FIG. 10   d  showing an axial spring mounted in the groove with two spring coils deflected and one not deflected as yet; 
         FIGS. 11   a - 11   e  shows a face compression axial spring retained by inside angular sidewall; 
         FIGS. 12   a - 12   e  show a latching radial spring in a radial groove designed for high disconnect to insertion ratio shown radially loaded and causing the coils to turn to provide axial load to reduce axial movement. GW&gt;CH; 
         FIGS. 13   a - 13   e  show a latching axial spring in an axial groove designed for high disconnect to insertion ratio with the spring shown in an axially loaded position to limit axial play, the spring coils assuming a turn angle position that increases force and provides higher conductivity with reduced variability; 
         FIGS. 14   a - 14   k  show a spring with ends threaded to form a continuous spring-ring without welding joining, which is different than the design indicated in  FIG. 1 ; 
         FIGS. 15   a - 15   k  show a spring with end joined by a male hook and step-down circular female end to form a continuous circular spring-ring without welding; 
         FIGS. 16   a - 16   l  show a spring with the coil ends connected by interlacing the end coils to form a continuous spring-ring without welding or joining; 
         FIGS. 17   a - 17   d  show a spring with coils ends butted inside the groove forming a spring-ring without welding; and 
         FIGS. 18   a - 18   f  show an unwelded spring ring and to be housed in a flat bottom housing groove, front angle in the front, showing the various different designs that could be used to retain the spring in a groove that can be a housing groove or a piston groove. 
     
    
    
     DETAILED DESCRIPTION 
     Connectors using latching applications have been described extensively, as for example, U.S. Pat. Nos. 4,974,821, 5,139,276, 5,082,390, 5,545,842, 5,411,348 and others. 
     Groove configurations have been divided in two types: one type with a spring retained in a housing described in Tables 1a-1g and another with the spring retained in a shaft described in Tables 2a-2g. 
     Definitions 
     A definition of terms utilized in the present application is appropriate. 
     Definition of a radial canted coil spring. A radial canted coil spring has its compression force perpendicular or radial to the centerline of the arc or ring. 
     Definition of axial canted coil spring. An axial canted coil spring has its compression force parallel or axial to the centerline of the arc or ring. 
     The spring can also assume various angular geometries, varying from 0 to 90 degrees and can assume a concave or a convex position in relation to the centerline of the spring. 
     Definition of concave and convex. For the purpose of this patent application, concave and convex are defined as follows: The position that a canted coil spring assumes when a radial or axial spring is assembled into a housing and positioned by-passing a piston through the ID so that the ID is forward of the centerline is in a convex position. 
     When the spring is assembled into the piston, upon passing the piston through a housing, the spring is positioned by the housing so that the OD of the spring is behind the centerline of the spring is in a convex position. 
     The spring-rings can also be extended for insertion into the groove or compressed into the groove. Extension of the spring consists of making the spring ID larger by stretching or gartering the ID of the spring to assume a new position when assembled into a groove or the spring can also be made larger than the groove cavity diameter and then compressed the groove. 
     Canted coil springs are available in radial and axial applications. Generally, a radial spring is assembled so that it is loaded radially. An axial spring is generally assembled into a cavity so that the radial force is applied along the major axis of the coil, while the coils are compressed axially and deflect axially along the minor axis of the coil. 
     Radial springs. Radial springs can have the coils canting counterclockwise (Table 1a, row 2, column 13) or clockwise (Table 1a, row 3, column 13). When the coils cant counterclockwise, the front angle is in the front (row 2, column 13). When the coils cant clockwise (Table 1a, row 3, column 13), the back angle is in the front. Upon inserting a pin or shaft through the inside diameter of the spring with the spring mounted in the housing in a counterclockwise position (Table 1a, row 2, columns 2, 3, 5), the shaft will come in contact with the front angle of the coil and the force developed during insertion will be less than when compressing the back angle from a spring in a clockwise position. The degree of insertion force will vary depending on various factors. The running force will be about the same (Table 1a, row 2, columns 6, 8). 
     RUNNING FORCE. Running force is the frictional force that is produced when a constant diameter portion of the pin is passed through the spring. 
     Axial springs may also be assembled into a cavity whose groove width is smaller than the coil height (Table 1a, row 5, columns 2, 3, 5, 6, 7 and 8). Assembly can be done by inserting spring (Table 1a, row 5, column 13) into the cavity or by taking the radial spring (Table 1a, row 7, column 13) and turning the spring coils clockwise 90° into a clockwise axial spring (Table 1a, row 7, column 15) and inserting into the cavity. Under such conditions, the spring will assume an axial position, provided the groove width is smaller than the coil height. Under such conditions, the insertion and running force will be slightly higher than when an axial spring is assembled into the same cavity. The reason is that upon turning the radial spring at assembly, a higher radial force is created, requiring a higher insertion and running force. 
     Axial springs RF and F definition. Axial springs can be RF (Table 1a, row 5, column 13) with the coils canting clockwise or they can be F (Table 1a, row 6, column 13) with the coils canting counterclockwise. An RF spring is defined as one in which the spring ring has the back angle at the ID of the coils (Table 1a, row 5, column 12) with the front angle on the OD of the coils. An F spring (Table 1a, row 6, column 13) has the back angle on the OD and the front angle at the ID of the coils. 
     Turn angle springs are shown in Table 1e, row 10, column 13, Table 1f, rows 2-5, column 13. The springs can be made with turn angles between 0 and 90 degrees. This spring can have a concave direction (Table 1a, row 5, column 6) or a convex direction (Table 1a, row 5, column 8) when assembled into the cavity, depending on the direction in which the pin is inserted. This will affect the insertion and running force. 
     F type axial springs always develop higher insertion and running forces than RF springs. The reason is that in an F spring the back angle is always located at the OD of the spring, which produces higher forces. 
     Definition of Point of Contact. The point of load where the force is applied on the coil during unlatching or disconnecting of the two mating parts. (Table 1a, row 2, column 11, row 5, column 11). 
     Definition of “end of the major axis of the coil.” The point at the end of the major axis of the coil. (Table 1a, row 2, column 2 and row 5, column 2). 
     Types of grooves that may be used. 
     Flat groove. (Table 1a, row 2, column 4) The simplest type of groove is one that has a flat groove with the groove width larger than the coil width of the spring. In such case, the force is applied radially. 
     ‘V’ bottom groove. (Table 1a, row 4, column 4) This type of groove retains the spring better in the cavity by reducing axial movement and increasing the points of contact. This enhances electrical conductivity and reduces the variability of the conductivity. The groove width is larger than the coil width. The spring force is applied radially. 
     Grooves for axial springs. (Table 1a, row 5, column 2) Grooves for axial springs are designed to better retain the spring at assembly. In such cases, the groove width is smaller than the coil height. At assembly, the spring is compressed along the minor axis axially and upon the insertion of a pin or shaft through the ID of the spring the spring, the coils deflect along the minor axis axially. 
     There are variations of these grooves from a flat bottom groove to a tapered bottom groove. 
     Axial springs using flat bottom groove. In such cases, the degree of deflection available on the spring is reduced compared to a radial spring, depending on the interference that occurs between the coil height and the groove width. 
     The greater the interference between the spring coil height and the groove, the higher the force to deflect the coils and the higher the insertion and running forces. 
     In such cases, the spring is loaded radially upon passing a pin through the ID. The deflection occurs by turning the spring angularly in the direction of movement of the pin. An excessive amount of radial force may cause permanent damage to the spring because the spring coils have “no place to go” and butts. 
     Axial springs with grooves with a tapered bottom. (Table 1b, rows 7-9, column 2 through Table 1c, rows 2-7, column 2) A tapered bottom groove has the advantage that the spring deflects gradually compared to a flat bottom groove. When a pin is passed through the ID of the spring, it will deflect in the direction of motion. The running force depends on the direction of the pin and the type of spring. Lower forces will occur when the pin moves in a concave spring direction (Table 1b, row 5, column 6) and higher force when the pin moves in a convex spring direction (Table 1b, row 5, column 8). 
     Tapered bottom grooves have the advantage that the spring has a substantial degree of deflection, which occurs by compressing the spring radially, thus allowing for a greater degree of tolerance variation while remaining functional as compared to flat bottom grooves. 
     Mounting of groove. Grooves can be mounted in the piston or in the housing, depending on the application. Piston mounted grooves are described in Tables 2a-2g. 
     Expansion and contracting of springs. A radial spring ring can be expanded from a small inside diameter to a larger inside diameter and can also be compressed from a larger OD to a smaller OD by crowding the OD of the spring into the same cavity. When expanding a spring the back angle and front angles of the spring coils decrease, thus increasing the connecting and running forces. When compressing a radial spring OD into a cavity, which is smaller than the OD of the spring, the coils are deflected radially, causing the back and front angles to increase. The increase of these angles reduces the insertion and running forces when passing a pin through the ID of the spring. 
     The following patents and patent application are to be incorporated in this patent application as follows: 
     
         
         
           
             1) U.S. Pat. No. 4,893,795 sheet 2 FIGS. 4, 5A, 5B, 5C, 5D, 5E, 6A and 6B; 
             2) U.S. Pat. No. 4,876,781 sheet 2 and sheet 3 FIGS. 5A, 5B, and FIG. 6. 
             3) U.S. Pat. No. 4,974,821 page 3 FIGS. 8 and 9 
             4) U.S. Pat. No. 5,108,078 sheet 1 FIGS. 1 through 6 
             5) U.S. Pat. No. 5,139,243 page 1 and 2 FIGS. 1A, 1B, 2A, 2B and also FIG. 4A, 4B, 5A, and 5E 
             6) U.S. Pat. No. 5,139,276 sheet 3 FIGS. 10A, 10B, 10C, 11A, 11B, 12A, 12B, 12C, 13A, 13B, and 14 
             7) U.S. Pat. No. 5,082,390 sheet 2 and 3, FIGS. 4A, 4B, 5A, 5B, 6A, 6B, 7A, 7C, 8A, 8B 
             8) U.S. Pat. No. 5,091,606 sheets 11, 12, and 14. FIGS. 42, 43, 44, 45, 46, 47, 48, 48A, 48B, 49, 50A, 50B, 50C, 51A, 51B, 51C, 58A, 58B, 
             9) U.S. Pat. No. 5,545,842 sheets 1, 2, 3, and 5. FIGS. 1, 4, 6, 9, 13, 14, 19, 26A, 26B, 27A, 27B, 28A, 28B. 
             10) U.S. Pat. No. 5,411,348 sheets 2, 3, 4, 5, and 6. FIGS. 5A, 5C, 6A, 6C, 7A, 7C, 7D, 8A, 8B, 8C, 9A, 9C, 10C, 11, 12 and 17. 
             11) U.S. Pat. No. 5,615,870 Sheets 1-15, Sheets 17-23 with FIGS. 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 16, 17, 18, 19, 20, 21, 22, 23, 24, 25, 26, 27, 28, 29, 30, 31, 32, 33, 34, 35, 36, 37, 38, 39, 40, 41, 42, 43, 44, 45, 46, 47, 48, 49, 50, 51, 52, 53, 54, 55, 56, 57, 58, 59, 60, 61, 66, 67, 68, 69, 70, 71, 72, 73, 74, 75, 76, 77, 78, 79, 80, 81, 82, 83, 84, 85, 86, 87, 88, 92, 93, 94, 95, 96, 97, 98, 99, 100, 101, 102, 103, 104, 105, 106, 107, 108, 109, 110, 111, 112, 113, 114, 115, 116, 117, 118, 119, 120, 121, 123, 124, 125, 126, 127, 128, 129, 130, 131, 132, 133, 134, 135. 
             12) U.S. Pat. No. 5,791,638 Sheets 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 17, 18, 19, 20, 21, 22, 23. FIGS. 1-61 and 66-88 and 92-135. 
             13) U.S. Pat. No. 5,709,371, page 1, 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, 15, 17, 18, 19, 20, 21, 22, 23. FIGS. 1-61 and 66-88 and 
             14) Application for patent by Balsells entitled “Spring Holding Connectors” Customer Ser. No. 10/777,974 filed Feb. 12, 2004. 
           
         
       
    
     In general, Tables 1a-1g illustrate housing mounted designs for holding and other applications. These tables show 53 different types of grooves and spring geometries in which the spring is mounted in the housing, using different spring configurations and different groove variations, which result in different insertion and running forces. 
     Table 1a, row 2, columns 2-12 show a flat bottom groove with a radial spring. 
     Table 1a, row 2, column 2 shows an assembly with a spring mounted in a housing with a shaft moving forward axially. 
     Table 1a, row 2, column 3 shows the assembly in a latched position. 
     Table 1a, row 2, column 4 shows schematic of a flat bottom groove. 
     Table 1a, row 2, column 5 shows and enlarged portion of Table 1A, row 2, column 2. 
     Table 1a, row 2, column 6 shows the assembly in a hold running connect direction 
     Table 1a, row 2, column 7 shows an enlarged portion of Table 1a, row 2, column 3 in a latch position. 
     Table 1a, row 2, column 8 shows the assembly in a hold running disconnect direction. 
     Table 1a, row 2, column 9 shows the assembly returning to the inserting position. 
     Table 1a, row 2, column 10 shows an enlarged view of the point of contact between the coils and the shaft. 
     Table 1a, row 2, column 11 shows an enlarged view of Table 1a, row 2, column 3. 
     Table 1a, row 2, column 12 shows a cross section of the radial spring with the dot indicating the front angle. 
     Table 1a, row 2, column 13 shows the spring in a free position and shows a front view of the canted coil counterclockwise radial spring with the front angle in front. 
     Table 1a, row 3, columns 2-12 show a spring mounted 180° from that shows in Table 1a, row 2 in a clockwise position. Table 1a, row 4, columns 1-12 show a V-bottom groove with a counterclockwise radial spring. 
     Table 1a, row 5, columns 1-12 show a flat bottom axial groove with an RF axial spring. The groove width is smaller than the coil height and the point of contact is closer to the centerline of the major axis of the spring coil. The closer the point of contact is to the point at the end of the major axis of the coil, the higher the force required to disconnect in a convex direction. (Table 1a, row 5, columns 7-8).
 
Table 1a, row 6, columns 2-12 show a flat bottom groove with an F axial spring. The groove width is smaller than the coil height.
 
Table 1a, rows 7-8 and Table 1b, row 9 show a radial spring turned into an axial spring by assembling this spring into a cavity in an axial position.
 
     More specifically, Table 1a, row 6 shows a flat bottom axial groove with counterclockwise radial spring mounted in an RF axial position. The groove width is smaller than the coil height. 
     Table 1a, row 8 is a flat bottom groove with a counterclockwise radial spring mounted in an F axial position. 
     Table 1a, row 9 is a flat bottom groove with a clockwise radial spring mounted in an RF axial position. The groove width smaller than the coil height, and 
     Table 1b, row 2 shows a flat bottom axial groove with clockwise radial spring mounted in F axial position. Groove width smaller than the coil height. 
     Table 1b, row 3 shows a V bottom groove with an RF axial spring. The groove width is smaller than the coil height. 
     Table 1b, row 4 shows a flat bottom groove with an RF axial spring with a groove width larger than the coil height. Making the groove width larger than the coil heights allows the point of contact to move further away from the point at the end of the major axis of the coil at disconnect thus decreasing the force.
 
Table 1b, row 5 shows a V bottom flat groove with RF axial spring. The groove width is larger than the coil height. (GW&gt;CH)
 
Table 1b, row 6 shows a design like Table 1b, row 5, except that the RF axial spring has offset coils that fit into the groove. The offset coils allow partial contact holding within the groove at different intervals along the groove diameter walls, and the coils are deflected axially at different points of the groove on both sides sufficiently to retain the spring in place. The offset coils increase the total axial coil height, which helps retain the spring inside the groove. The insertion and running forces are also reduced compared to Table 1b, row 5 where the groove width is smaller than the coil height. The difference in force is illustrated in Table 1b, row 6, column 12, where force versus shaft travel distance is shown illustrating the force developed.
 
     Table 1b, row 6, column 13 and 14 shows the offset coils in a free position. 
     Table 1b, row 6, column 11 shows the point of contact in relation to the point at the end of the major axis of the coils with the point of contact further away from the major axis of the coil thus decreasing the force required to disconnect. This can be compared with Table 1b, row 8, column 11 whereby the point of contact is closer to the point at the end of the major axis of the coil, thus requiring a substantially higher force to disconnect. 
     Table 1b, row 7 shows an axial RF spring with a tapered bottom groove that positions the point of contact (Table 1b, row 7, column 11) closer to the end point at the end of the major axis of the coil than in Table 1b, row 6, column 11, thus requiring a greater force to disconnect.
 
Table 1b, row 8 shows a tapered bottom groove of a different configuration but similar to Table 1b, row 7 with an RF axial spring with a groove width smaller than the coil height. The groove configuration positions the point of contact closer to the end point at the end of the major axis of the coil. An axial RF spring is used in this design.
 
     Table 1b, row 9 shows a tapered bottom groove with RF axial spring with a groove width smaller than the coil height. 
     The point of contact is positioned at the end point of the major axis of the coil and disconnect is not possible as the force is applied along the major axis since the spring will not compress along that axis. 
     Table 1c, row 2 shows a tapered bottom groove with an axial spring mounted in the groove. The position of the spring is such that the centerline along the minor axis is slightly above the bore, which results in less deflection of the spring, thus positioning the point of contact further away from the end point of the major axis of the coil, resulting in a lower disconnect force. 
     Table 1c, row 3 shows a tapered bottom groove with an axial spring mounted in the groove. The groove is shown with a 25-degree angle. By increasing the angle, the distance from the end of the major axis of the coil to the point of contact increases (Table 1c, row 3, column 11 compared to Table 1b, row 8, column 11), resulting in lower connect and disconnect forces. On the other hand, decreasing the taper angle will bring the point of contact closer to the end of the major axis of the coil, resulting in higher connect and disconnect forces. Increasing the groove angle will increase the spring deflection which will increase the running force. 
     Table 1c, row 4 shows a tapered bottom groove with an RF axial spring with the shaft inserted in the opposite direction. The groove width is smaller than the coil height. In this case, again, the point of contact at the point at the end of the major axis of the coil and no deflection exists and a disconnect is not possible. 
     Insertion force in this direction will cause the spring coil to turn counter clockwise thus applying a force along the major axis of the coil and the spring will not deflect along the major axis causing damage to the spring. 
     Table 1c, row 5 shows a tapered bottom groove with 45° turn angle spring with the shaft inserted in the convex direction. The groove width is smaller than the coil width. The angular spring deflects axially. 
     Table 1c, row 6 shows a tapered bottom groove with an RF axial spring filled with an elastomer with a hollow center. The groove width is smaller than the coil height (GW&lt;CH). 
     Table 1c, row 7 Shows a tapered bottom groove with an RF axial spring filled with an elastomer solid, as in Table 1c, row 6 with the groove width smaller than the coil height (GW&lt;CH). 
     Table 1c, row 8 shows a step round flat bottom groove with an RF axial spring groove with the width smaller than the coil height. This design has a groove with a point of contact that scrapes the wire as the coil moves, removing oxides that may be formed on the surface of the wire. The groove has been designed to provide a lower force at disconnect by increasing the distance between the point of contact and the point at the end of the major axis of the coil.
 
Table 1c, row 9 shows an inverted V bottom groove with RF axial spring. The groove width is smaller than the coil height.
 
Table 1d, row 2 shows a tapered bottom groove with a counterclockwise radial spring mounted in a RF position. The groove width is smaller than the coil height. Notice the position of the point of contact with respect to the end point at the end of the major axis of the coil. The closer the point of contact to the end point at the end of the major axis of the coil the higher the force required to disconnect.
 
Table 1d, row 3 shows a tapered bottom groove with a counterclockwise radial spring mounted in an F axial position. The groove width is smaller than the coil height.
 
Table 1d, row 4 shows a tapered bottom groove with a clockwise radial spring mounted in an RF axial position. The groove width is smaller than the coil height.
 
Table 1d, row 5 shows a tapered bottom groove with a clockwise radial spring mounted in an F axial position. The groove width is smaller than the coil height.
 
Table 1d, row 6 shows a dovetail groove with a counterclockwise radial spring.
 
Table 1d, row 7 shows a special groove with a counterclockwise radial spring.
 
Table 1d, row 8 shows an angle of zero to 22½ degrees flat and tapered bottom groove with a counterclockwise radial spring. The groove width is greater than the coil width. The spring in latching will turn clockwise positioning the coil to reduce the force required to disconnect by positioning the point of contact further away from the end of the end point at the end of the major axis of the coil.
 
Table 1d, row 9 shows an angle of 0 to 22½ degrees. The piston groove has a flat and a tapered bottom with a clockwise spring. The spring has an ID to coil height ratio smaller than 4. Under load, this spring has a higher torsional force that requires a higher force to connect or disconnect the shaft. Upon latching, the spring turns clockwise, moving the point of contact closer to the end of the major axis of the coil (Table 1d, row 9, column 7 and Table 1d, row 9, column 11) thus increasing the force to disconnect.
 
Table 1e, row 2 is like Table 1d, row 9 except that in this case, the spring groove has an ID to coil height ratio greater than 4, thus the radial force applied to the spring at connect or disconnect is substantially lower. As the ratio of the ID of the spring to the coil height increases, the force required to connect or disconnect decreases due to a lower radial force.
 
Table 1e, row 3 has an angle groove with a 0° to 22.5° piston groove angle similar to  FIG. 3  except that the piston groove has a ‘V’ bottom groove instead of a ‘V’ bottom groove with a flat. The housing has a ‘V’ bottom groove with a flat at the bottom of the groove. This design permits for specific load points at connect-latched position.
 
Table 1e, row 4 shows a groove angle 30°/22½° bottom groove with a counterclockwise radial spring. The groove width is greater than the coil width. By changing the groove angle, the distance between the point of contact and the point at the end of the major axis of the coil is increased, reducing the force at disconnect.
 
Table 1e, row 5 shows an angle 60°/22½° bottom groove with a counterclockwise radial spring. The groove width is greater than the coil width.
 
Table 1e, row 6 shows a special V type bottom with a 23° and 60° angle with a counterclockwise radial spring. The groove width greater than the coil width.
 
Table 1e, row 7 shows a V type bottom groove with 23° and 60° angles like Table 1e, row 6 with a counterclockwise radial spring. The groove width is greater than the coil width. By moving the shaft forward and then back it causes the spring to turn so the point of contact is closer to the point at the end of the major axis of the coil, increasing the force required to disconnect. When the direction of latching is reversed, the piston is traveling in the direction of the back angle in Table 1e, row 8, column 2, as opposed to traveling in the direction of the front angle in Table 1e, row 7, column 2. The increased force increases the turning of the spring, thus increasing the distance between the point of contact and the end point of the major axis, decreasing the force required to disconnect or unlatch. Compare Table 1e, row 7, column 8 showing the piston moving forward and the position of the point of contact “A” with the position of the point of contact Table 1e, row 7, column 7.
 
Table 1e, row 9 shows a special V bottom type groove with 22° and 60° angles with a radial spring The contact point is close to the point at the end of the major axis of the coil for a high disconnect force.
 
Table 1e, row 10 through Table 1f, row 5 show turn angle springs, assembled in different groove designs. Notice the point of contact position in relation to the POINT AT THE END OF THE major axis of the coil.
 
     More specifically, Table 1e, row 10 shows a special V-bottom with 23° and 60° angles with a 20° turn angle spring. 
     Table 1f, row 2 shows a special V-bottom with 30° and 60° angles with a 20° turn angle spring. 
     Table 1f, row 3 shows a special V-bottom with 60° and 49° angles with a 20° turn angle spring. 
     Table 1f, row 4 shows a special groove with a 45° turn angle spring. In this case, the point of contact is closer to the point at the end of the minor axis of the coil. Upon insertion, the pin will cause the spring to expand radially and causing the coil to deflect along the minor axis and causing the spring coils to turn counterclockwise to connect. At disconnect the spring coils will deflect along the minor axis and the coils will continue to turn counterclockwise to disconnect. The spring coils will turn clockwise to its original position when the force acting on the spring is released.
 
Table 1f, row 5 shows a special tapered groove with a 30° angle with a 45° angle at the piston groove. Notice the point of contact in relation to the point at the end of the major axis of the coil.
 
Table 1f, rows 6-8 show an axial spring mounted in a tapered bottom groove.
 
     More specifically, Table 1f, row 6 shows an angular groove with an RF axial spring with a groove depth greater than the coil width. Notice the position of the point of contact at disconnect with the coil diameter expands radially permitting disconnect. 
     Table 1f, row 7 shows a groove similar to  FIG. 3   a , but with a tapered angle on one side of the groove. 
     Table 1f, row 8 shows a symmetrical angle groove with an RF axial spring. The groove depth is greater than the coil width. 
     Table 1f, row 9 shows a flat bottom-housing groove with a counterclockwise radial spring. The groove width is greater than the coil height. In this case, the piston has a step groove. 
     Table 1g, rows 2-6 show various methods of mounting a panel on a housing, using a length of spring whose groove can be mounted on the housing or on the panel and such groove has a groove width smaller than the coil height so that the spring can be retained in such groove.
 
Table 1g, row 2 shows a panel-mounted design with length of spring with axial loading and holding.
 
Table 1g, row 2, column 2 shows the panel in an inserting position. Table 1g, row 2, column 3 shows the panel in a connected position. Table 1g, row 2, column 4 shows a schematic of the groove design. Table 1g, row 2, column 5 shows the spring being inserted into the cavity. Table 1g, row 2, column 7 shows the spring in a holding position. Table 1g, row 2, column 11 shows an enlarged view of Table 1g, row 2, column 7.
 
Table 1g, row 3 shows a panel mounting design with length of spring with some axial loading and latching, using a flat tapered groove. The groove width is smaller than the coil height. This particular design will permit axial movement of the panel. Table 1g, row 2, column 3 shows the design in a latch position, which can permit axial movement. Table 1g, row 3, column 8 shows an enlarged view of the latch position. Table 1g, row 3, column 5 shows the point in contact in relation to the end major axis of the coil.
 
Table 1g, row 4 shows a panel mounting design with length of spring with latching, which will permit axial movement of the panel and locking, using a rectangular groove on the panel with the groove width smaller than the coil height.
 
Table 1g, row 4, column 3 shows the design in a latch axial position, permitting some axial movement. Table 1g, row 4, column 5 shows an enlarged view of the latch position. Table 1g, row 4, column 9 shows a latch locked position to disconnect. Table 1g, row 4, column 11 shows an enlarged view of the point of contact with end of major axis of the coil at locking.
 
Table 1g, row 5 shows a panel mounting with length of spring with axial loading and latching. Groove width smaller than the coil height.
 
Table 1g, row 5, column 2 shows the panel in an inserting position and Table 1g, row 5, column 3 in a latched position with the spring retained in the groove mounted in the housing with the grooves offset from each other. The grooves are offset to provide axial loading in the latched position. In this case, the panel has a V-groove design. Notice the axially loaded position of the spring to prevent axial movement when in a connected-latched position.
 
Table 1g, row 6 shows a panel assembly similar to Table 1g, row 5 except that the panel has a step flat bottom groove instead of a V-bottom type groove and the housing has a flat tapered bottom groove and it is axially loaded in the connect position. Disconnect in the axial position will not be possible because as the panel is pulled it causes the spring to turn, applying the disconnect component force at the end of the major axis of the coil where no deflection occurs.
 
The descriptions illustrated in Tables 1g, rows 2-6 show the holding, latching, and locking in the axial position. Separation of the panel from the housing can be done by sliding the panel longitudinally.
 
These designs indicated in Table 1g, rows 2-6 show a panel-mounted design; however, the design could also be applicable to other designs, such as cylindrical, rectangular, elliptical or other types of surfaces. All designs are shown with GW&lt;CH; however the groove could be made wider to be GW&lt;CH with lower connect-disconnect force.
 
Table 1g, rows 7-9 are similar to Table 1e, row 3, show different methods of retaining the spring in the cavity.
 
Table 1g, row 7 shows a rectangular washer retaining the spring in position.
 
Table 1g, row 8 shows a snap ring retaining the spring in position.
 
Table 1g, row 9 shows a washer retained in position by rolling over a portion of the housing on to the washer housing to form the retaining groove.
 
The designs are shown with specific dimensions, angles and groove configurations. These values can be changed to other angles and groove configurations while achieving the results indicated.
 
Piston Mounted Designs for Latching Applications.
 
     Table 2a-2g show various designs with the spring mounted in the piston in latching applications. In essence, these applications are similar to the ones that are described in Tables 1a-1g except that the spring is mounted in the piston and it encompasses 48 variations of groove designs. 
     Table 2a, row 2 shows a flat bottom groove with counterclockwise radial spring with a groove width greater than the coil width. Table 2a, columns 2-9, show different assemblies of the spring and grooves and the spring in various positions. 
     Table 2a, row 2, column 2 shows the assembly in an insert position. 
     Table 2a, row 2, column 3 shows the assembly in a latch position. 
     Table 2a, row 2, column 4 shows the cross section of the flat bottom groove. 
     Table 2a, row 2, column 5 shows an enlarged view of Table 2a, row 2, column 2. 
     Table 2a, row 2, column 6 shows the position of the spring in a hold-RUNNING position with the spring deflected along the minor axis. 
     Table 2a, row 2, column 7 shows an enlarged position of Table 2a, row 2, column 3 in a latched-connect position moving in a disconnect direction relative to the end point of the major axis. 
     Table 2a, row 2, column 8 shows the assembly in hold-disconnect direction. 
     Table 2a, row 2, column 9 shows the assembly returning to the inserting position. 
     Table 2a, row 2, column 10 shows the spring in a free position. 
     Table 2a, row 2, column 11 shows a partial enlarged view of Table 2a, row 2, column 7. 
     Table 2a, row 2, column 12 shows a cross sectional view of the spring showing the position of the front angle. 
     Table 2a, row 2, column 13 shows a front view of the spring in a counterclockwise with the radial spring front angle in the front. 
     Table 2a, row 3, is the same position as Table 2a, row 2 except that the spring has been turned around 180°. 
     Table 2a, row 4 shows a V-bottom groove with a counterclockwise radial spring with a groove width greater than the coil width. 
     Table 2a, row 5 shows a flat bottom axial groove with an RF axial spring. The groove width is smaller than the coil height. The point of contact is close to the end point of the major axis of the coil, requiring a high force to disconnect. 
     Table 2a, row 6 shows a design as in Table 2a, row 5 except it uses an F spring. 
     Table 2a, rows 7-9 and Table 2b, row 2 shows a radial spring turned into an axial spring, using a flat bottom groove. 
     Table 2b, row 3 shows a V-bottom groove with an RF axial spring. The groove width is smaller than the coil height. 
     Table 2b, row 4 shows a flat bottom groove with an RF axial spring. The groove width is greater than the coil height, thus resulting in lower disconnect force. 
     Table 2b, row 5 shows a V-bottom tapered groove with an RF axial spring. The groove width is greater than the coil height. 
     Table 2b, row 6 shows a design like Table 2b, row 8, except that the RF axial spring has offset coils that fit into the groove. The offset coils allow partial contact holding within the groove at different intervals along the groove diameter walls, and the coils are deflected axially at different points of the groove on both sides sufficiently to retain the spring in place. The offset coils increase the total axial coil height, which helps retain the spring inside the groove. The insertion and running forces are also reduced compared to Table 2b, row 8 where the groove width is smaller than the coil height. The difference in force is illustrated in Table 2b, row 5, column 12, where we show force versus shaft travel distance, illustrating the force developed in Table 2b, row 7 and in Table 2b, row 6.
 
Table 2b, row 6, column 12 shows a diagram Force vs. Shaft Travel Distance that compares the force developed by Table 2b, row 7 vs. Table 2b, row 6.
 
Table 2b, row 6, columns 14-15 shows the offset coils in a free position.
 
Table 2b, row 6, column 11 shows the point of contact in relation to the point at the end of the major axis of the coils with the point of contact further away from the end point of the major axis of the coil thus decreasing the force required to disconnect. This can be compared with Table 2b, row 7, column 11 whereby the point of contact is closer to the end point of the major axis of the coil, thus requiring a substantially higher force to disconnect.
 
Table 2b, row 7 shows an axial RF spring with a tapered bottom groove that positions the point of contact (Table 2b, row 7, column 11) closer to the end point of the major axis of the coil than in Table 2b, row 6, column 11, thus requiring a greater force to disconnect.
 
Table 2b, row 8 shows a tapered bottom groove of a different configuration but similar to Table 2b, row 7 with an RF axial spring with a groove width smaller than the coil height. The groove configuration positions the point of contact closer to the end point at the end of the major axis of the coil. An axial RF spring is used in this design.
 
     Table 2b, row 9 shows a tapered bottom groove with RF axial spring with a groove width smaller than the coil height. The end point of contact is positioned at the point of contact at the end point of the major axis of the coil and disconnect is not possible as the force is applied along the major axis since the spring will not compress along that axis. 
     Table 2c, row 2 shows a tapered bottom groove with an axial spring mounted in the groove. The position of the spring is such that the centerline along the minor axis is slightly above the bore, thus positioning the point of contact further away from the end point of the major axis of the coil, resulting in a lower disconnect force. 
     Table 2c, row 3 shows a tapered bottom groove with an axial spring mounted in the groove. The groove is shown with a 25-degree angle. By increasing the angle, the distance from the end point of the major axis of the coil to the point of contact increases (Table 2c, row 3, column 11 compared to Table 2b, row 9, column 11), resulting in lower connect and disconnect forces. On the other hand, decreasing the taper angle will bring the point of contact closer to the end point of the major axis of the coil, resulting in higher connect and disconnect forces. Increasing the groove angle will increase the spring deflection which will increase the running force (Table 1c, row 2, column 6, Table 1c, row 3, column 8). 
     Table 2c, row 4 shows a tapered bottom groove with an RF axial spring with the shaft inserted in the opposite direction. The groove width is smaller than the coil height. In this case, again, the point of contact is at the end point of the major axis of the coil and no deflection exists and a disconnect is not possible.
 
Table 2c, row 5 shows a tapered bottom groove with 45° turn angle spring with the shaft inserted in the convex direction. The groove width is smaller than the coil width. The angular spring deflects axially.
 
Table 2c, row 6 shows a tapered bottom groove with an RF axial spring filled with an elastomer with a hollow center. The groove width is smaller than the coil height (GW&lt;CH).
 
Table 2c, row 7 shows a tapered bottom groove with an RF axial spring filled with an elastomer solid, as in Table 2c, row 6 with the groove width smaller than the coil height (GW&lt;CH).
 
Table 2c, row 8 shows a step round flat bottom groove with an RF axial spring groove with the width smaller than the coil height. This design has a groove with a point of contact that scrapes the wire as the coil moves, removing oxides that may be formed on the surface of the wire. The groove has been designed to provide a lower force at disconnect by increasing the distance between the point of contact and the end point of the major axis of the coil.
 
Table 2c, row 9 shows an inverted V bottom groove with an RF axial spring. The groove width is smaller than the coil height.
 
Table 2d, row 2 shows a tapered bottom groove with a counterclockwise radial spring mounted in an RF position. The groove width is smaller than the coil height. Notice the position of the point of contact with respect to the end point at the end of the major axis of the coil. The closer the point of contact to the end point of the major axis of the coil, the higher the force required to disconnect.
 
Table 2d, row 3 shows a tapered bottom groove with a counterclockwise radial spring mounted in an F axial position. The groove width is smaller than the coil height.
 
Table 2d, row 4 shows a tapered bottom groove with a clockwise radial spring mounted in an RF axial position. The groove width is smaller than the coil height.
 
Table 2d, row 5 shows a tapered bottom groove with a clockwise radial spring mounted in an F axial position. The groove width is smaller than the coil height.
 
Table 2d, row 6 shows a dovetail groove with a counterclockwise radial spring.
 
Table 2d, row 7 shows a special groove with a counterclockwise radial spring.
 
Table 2d, row 8 shows an angle of zero to 22½ degrees flat and tapered bottom groove with a counterclockwise radial spring. The groove width is greater than the coil width. The spring in latching will turn clockwise positioning the coil to reduce the force required to disconnect by positioning the point of contact further away from the end of the end point at the end of the major axis of the coil.
 
Table 2d, row 9 shows an angle of 0 to 22½ degrees. The piston groove has a flat and a tapered bottom with a clockwise spring. The spring has an ID to coil height ratio smaller than 4. Under load, this spring has a higher torsional force that requires a higher force to connect or disconnect the shaft. Upon latching, the spring turns clockwise, moving the point of contact closer to the end point of the major axis of the coil (Table 2d, row 9 column 7, column 11) thus increasing the force to disconnect.
 
Table 2e, row 2 is like Table 2d, row 9 except that in this case, the spring groove has an ID to coil height ratio greater than 4, thus the torsional force applied to the spring at connect or disconnect is substantially lower. As the ratio of the ID of the spring to the coil height increases, the force required to connect or disconnect decreases due to a lower torsional force.
 
Table 2e, row 3 has an angle groove with a 0° to 22.5° piston groove angle similar to Table 2a, row 4 except that the piston groove in Table 2e, row 3 has a ‘V’ bottom groove instead of a ‘V’ bottom groove with a flat. The housing in Table 2e, row 3 has a ‘V’ bottom groove with a flat at the bottom of the groove. This design permits for specific load points at connect-latched position.
 
Table 2e, row 4 shows a groove angle 30°/22½° bottom groove with a counterclockwise radial spring. The groove width is greater than the coil width. By changing the groove angle, the distance between the point of contact and the end point of the major axis of the coil is increased, reducing the force at disconnect.
 
Table 2e, row 5 shows an angle 60°/22½° bottom groove with a counterclockwise radial spring. The groove width is greater than the coil width.
 
Table 2e, row 6 shows a special V type bottom with a 23° and 60° angle with a counterclockwise radial spring. The groove width is greater than the coil width.
 
Table 2e, rows 7-8 show a V type bottom groove with 23° and 60° angles like Table 2e, row 6 with a counterclockwise radial spring. The groove width is greater than the coil width. By moving the shaft forward and then back we cause the spring to turn so the point of contact is closer to the end point at the end of the major axis of the coil, increasing the force required to disconnect. When the direction of latching is reversed, the piston is traveling in the direction of the back angle in Table 1e, row 7, as opposed to traveling in the direction of the front angle in Table 1e, row 6. The increased force increases the turning of the spring, thus increasing the distance between the point of contact and the end point of the major axis, increasing the force required to disconnect or unlatch. Compare Table 2e, row 7, column 8 showing the piston moving forward and the position of the point of contact “A” with the position of the point of contact Table 2e, row 8, column 7.
 
Table 2e, row 9 shows a special V bottom type groove with 22° and 60° angles with a radial spring. The contact point is close to the end point at the end of the major axis of the coil for a higher disconnect force.
 
Table 1f, rows 2-6 show turn angle springs, assembled in different groove designs. Notice the point of contact position in relation to the end point of the major axis of the coil.
 
Table 2f, row 2 shows a special V-bottom with 23° and 60° angles with a 20° turn angle spring.
 
Table 2f, row 3 shows a special V-bottom with 30° and 60° angles with a 20° turn angle spring.
 
Table 2f, row 4 shows a special V-bottom with 30° and 49° angles with a 20° turn angle spring.
 
Table 2f, row 5 shows a special groove with a 45° turn angle spring. In this case, the point of contact is closer to the end point at the end of the minor axis of the coil. Upon insertion, the pin will cause the spring to contract radially (Table 2f, row 5, column 2) and causing the coil to deflect along the minor axis (Table 2f, row 5, column 6) and causing the spring coils to turn counterclockwise to connect (Table 2f, row 5, column 7). At disconnect the spring coils will deflect along the minor axis and the coils will continue to turn counterclockwise to disconnect (Table 2f, row 5, column 8). The spring coils will turn clockwise to its original position (Table 2f, row 5, column 9) when the force acting on the spring is released.
 
Table 2f, row 6 shows a special tapered groove with a 30° angle with a 45° angle at the piston groove. Notice the point of contact in relation to the end point at the end of the major axis of the coil.
 
Table 2f, row 7 shows a flat bottom-housing groove with a counterclockwise radial spring. The groove width is greater than the coil height. In this case, the piston has a step groove.
 
Table 2f, row 8 shows a panel mounted design with length of spring with axial loading and holding.
 
Table 2f, row 8, column 2 shows the panel in an insert position. Table 2f, row 8, column 3 shows the panel in a connected position. Table 2f, row 8, column 4 shows a schematic of the groove design. Table 2f, row 8, column 5 shows the spring being inserted into the cavity. Table 2f, row 5, column 7 shows the spring in a holding position. Table 2f, row 8, column 11 shows an enlarged view of Table 2f, row 5, column 7 with the panel bottoming.
 
Table 2f, row 9 shows a panel mounting design with length of spring with some axial loading and latching, using a flat tapered groove. The groove width is smaller than the coil height. This particular design will permit axial movement of the panel. Table 2f, row 9, column 3 shows the design in a latch position, which will permit axial movement. Table 2f, row 9, column 7 shows an enlarged view of the latch position.
 
Table 2f, row 9, column 11 shows the point in contact in relation to the end point of the major axis of the coil.
 
Table 2g, row 2 shows a panel mounting design with length of spring that will permit axial movement of the panel and locking, using a rectangular groove on the housing with the groove width smaller than the coil height.
 
Table 2g, row 2, column 3 shows the design in a latch axial position, permitting some axial movement. Table 2g, row 2, column 7 shows an enlarged view of the latch locking means and Table 2g, row 5, column 10 shows an enlarged view of the point of contact with end of major axis of the coil.
 
Table 2g, row 3 shows a panel mounted design using a length of spring. The groove width is smaller than the coil height. Table 2g, row 3, column 2 shows the panel in an inserting position and Table 2g, row 3, column 3 in a latched position with the spring retained in the groove mounted in the housing with the grooves offset from each other. The grooves are offset to provide axial loading in the latched position. In this case, the panel has a V-groove design. Notice the axially loaded position of the spring to prevent axial movement when in a connected-latched position.
 
Table 2g, row 4 shows a panel assembly similar to Table 2g, row 3 except that the panel has a step flat bottom groove instead of a V-bottom type groove and the panel has a flat tapered bottom groove and it is axially loaded in the connect position. Disconnect in the axial position will not be possible because as the panel is pulled it causes the spring to turn, applying the disconnect component force at the end point of the major axis of the coil where no deflection occurs. The descriptions illustrated in Table 2f, row 8 through Table 2g, row 4 show the holding, latching, and locking in the axial position. Separation of the panel from the housing can be done by sliding the panel longitudinally.
 
The designs indicated in Table 2f, row 8 through Table 2g, row 4 show a panel mounted design; however the design could also be applicable to other designs, such as cylindrical, rectangular, elliptical or other types of surfaces. All designs are shown with GW&lt;CH; however the groove could be made wider to be GW&lt;CH with lower connect-disconnect force.
 
The designs are shown with specific dimensions, angles and groove configurations. These values can be changed to other angles and groove configurations while achieving the results indicated.
 
Spring Characteristics that Affect Performance
 
Spring design and installation factors
 
Using an axial spring to enhance retention of the spring in the groove or using a radial spring turned into an axial spring at installation.
 
Using an axial spring or a radial spring turned into an axial spring at installation to increase initial insertion, running and disconnect forces
 
Changing the coil width to coil height ratio
 
When the coil width to height ratio is close to one, the spring will turn easier reducing forces since the spring is round.
 
The smaller the coil width to coil height ratio, the smaller the back angle. The smaller the back angle, the higher the insertion force required when the piston is inserted in the spring into the back angle first. The opposite is true when the coil width to coil height ratio is reversed, i.e., the back angle is larger and the insertion forces are lower.
 
Using an F axial spring to increase the insertion running and disconnect forces compared to an RF spring.
 
Using an RF axial spring to reduce the insertion, running, and disconnect forces.
 
Using an offset axial spring to reduce the initial insertion running force, and disconnect forces.
 
Using a Length of Spring Mounted in an Axial Type Groove for Panel Applications
 
Using a spring with a ratio of ID to coil height to vary insertion, connect and the disconnect forces. As the ratio increases, the forces will decrease or vice versa as the ratio decreases the forces increase.
 
Using springs with varying turn angles to vary forces.
 
Using an axial spring with offset coils where the groove width is smaller than the coil height and addition of the coil height of the various coils to reduce insertion, running, connect, and disconnect forces and the ratio of connect to disconnect force.
 
The connect/disconnect forces decrease as the ratio of ID to coil height increases.
 
Using variable means to form the ring, ranging from threading the ends, latching the ends, interfacing the ends and butting as opposed to welding.
 
Varying the Device Geometry to Control the Forces
 
Designing the groove geometry to position the point of contact at disconnect relative to the end point of the major axis of the coil.
 
Positioning the end point of the spring major axis. The shorter the distance to the contact point, the higher the force required to disconnect.
 
Positioning the end point of the spring minor axis. The shorter the distance to the contact point, the lower the force required to disconnect.
 
Varying the groove design and insertion direction to vary the force.
 
Varying the groove geometry so that the spring torsional force in the latched position is in an axial direction thus increasing the force required to disconnect and minimizing axial play.
 
Position the latching grooves so that they are offset, causing the axial or radial spring coils to turn, introducing an axial force that reduces axial play and increases the force required to connect-disconnect. Table 1g, row 5, column 12; row 2, Table 2a, row 6, column 6 and row 8, column 6.
 
Position the geometry of the latching grooves that will cause the axial and radial spring coils to turn, increasing the force required to connect-disconnect.  FIGS. 12   e  and  13   e.  
 
The use of multiple springs and grooves to increase the forces and the current carrying capacity.
 
The forces vary according to the direction of the piston insertion.
 
Using threaded grooves with a spring length retained in the groove with a groove width smaller than the coil height.
 
     In accordance with the present invention to attain the maximum disconnect force, the point of contact should be as close as possible to the end of the major axis of the coil. Table 1 and Table 2a (rows 5, columns 7 and 11). 
     To attain the minimum disconnect force, the contact point, should be as close as possible to the end of the minor axis of the coil. Table 1a and Table 2a (row 1, column 7 and 11). 
     An axial spring with offset coils mounted in a housing with the groove width smaller than the addition of the coil height of the various coils, providing the following features: 
     Lower spring retention force. 
     Lower insertion force 
     Lower ratio of disconnect to connect 
     Lower ratio of disconnect to running force. 
     Reference Table 1b and Table 2b, row 6 vs. row 8. 
     Modification of the groove cavity that affects the position of the point of contact in relation to the end point of the major axis of the coil that affects the force required to disconnect, connect. Reference Table 1b and Table 2b, row 8 vs. row 9 and row 8, column 4 vs. row 9, column 4.
 
Modification of the groove cavity that affects the position of the point of contact in relation to the end of the major axis of the coil that affects the force required to disconnect-connect. Reference Table 1b and Table 2b, row 9 vs. Table 1c, 2c, row 2 and Table 1a, 2a, row 9, column 4 vs. Table 2a, 2c, row 2, column 4.
 
     The greater the interference between the coil height and the groove width, the higher the force required to disconnect. Table 1a and Table 2a (row 5, column 5 versus Table 1b, 2b, row 4, column 5) Table 1a, 2a, row 5, column 5 has interference between the coil height and the groove width while row 6 shows a clearance between the coil height and the groove width. 
     The higher the position of the coil centerline along the minor axis in relation to the groove depth. (Reference Table 1b and Table 2b, row 8, column 4 versus Table 1c, 2c, row 2, column 4) the higher the force required to disconnect. 
     The type of axial spring mounted in a housing or piston RF vs. F with RF having substantially more deflection but lower force compared to F. Reference Table 1a and Table 2a, row 5, column 2, column 5, and column 6 versus row 6, column 2, column 5 and column 6. 
     Manner and type of spring used affects the force required to connect/disconnect, using an axial RF or an F spring assembled into a groove whose groove width is smaller than the coil height versus a radial spring turned into an axial spring RF or F spring with coils canting clockwise or counterclockwise. Reference Table 1a and Table 2a, rows 5 and 6 versus rows 7, 8, 9 and Table 1b, 2b row 2 and also row 8 vs. Table 1d, 2d, rows 2-5. 
     Direction of movement of the piston or housing a radial spring that affects the force required to connect and disconnect. Reference Tables 1d, 2d, row 8, columns 2, 5, 7 and 11 vs. row 9, column 2, 5, 7, and 11 due to variation that exists between row 8 and row 9 between the point of contact and the point at the end of the major axis of the coil that results in substantial variation in forces. 
     The greater the insertion force of an axial spring into a groove whose GW&lt;CH, the higher the force required to disconnect (Reference Table 1b, 2b, row 8, column 5 vs. row 9, column 5). 
     Radial springs with different ratios of spring ID to coil height mounted in a housing or piston. Reference Table 1d, 2d, row 9 vs. Table 1e, 2e, row 2. The greater the ratio the lower the forces. 
     Variations of groove configuration affecting the connect-disconnect force by varying the groove angle. Reference Table 1e, row 3, column 5, column 7, column 11 vs. row 4, column 5, column 7, column 11. Such angle variation affects the distance between the point of contact and the point at the end of the major axis of the coil. The closer these two points the higher the force required to disconnect. 
     The effect of axially loading in the latched position or disconnect and the effect on initial disconnect force and travel. 
     A radial spring axially loaded in the latched position will require a higher initial disconnect force than a non-axially loaded spring. 
     An axially loaded axial spring will develop a higher initial force as shown in Table 1g, row 2, column 3, column 7, column 11 at disconnect than a non-axially loaded, and also Table 2f, row 8, column 3, column 7 and column 11. 
     Direction of the spring upon insertion as pointed out by the direction of the arrows. (Canted coil springs always deflect along the minor axis of the coil). The spring turns in the direction of the arrow, as shown in the following: 
       FIG. 1   a ,  1   b  forward in the direction of the arrow, Table 1a and Table 2a, row 2, column 8 and column 11 in the opposite direction. 
     An axial spring axially loaded in the latched position will require a higher disconnect force than a non-axially loaded spring. 
     Recognizing the direction in which the spring will deflect and may turn, assists in selecting the groove configuration. When the load is applied, the spring always deflects along the minor axis of the coil as it is the easiest way to deflect. The spring turns when the ratio of the coil width to the coil height is equal to 1 or greater. As the ratio increases, the ability of the spring coils to turn decreases, causing the spring to deflect instead of turn. Specifically, 
     A spring with different turn angles in conjunction with different grooves to vary the force to connect and disconnect. Turn angles permit the design of the grooves so that the spring does not have to be turned at assembly. Reference Table 1f and Table 2f, rows 2, columns 2, 7, 11 and row 6, columns 2, 5, 7 11; 
     Disconnect by expanding the ID of the spring and compressing the coils along the minor axis of the coils to affect insertion, connect and disconnect. Table 1f, rows 6-8; 
     Housing mounted grooves using a single groove versus a split groove. Note: all drawings in Table 1a show a split groove and Table 2a shows a single groove in row 4, column 2; 
     Panel mounted spring with groove width smaller than the coil height using a spring in length. Axial latching and axial loading the spring to prevent axial movement. Table 1g, rows 2-3, Table 2g, rows 8-9; 
     Axial loading the spring coils by offsetting the position of the grooves axially between the housing and shaft so as to create an axial load on the spring to reduce or eliminate movement between the shaft and housing. This configuration has a higher force as shown in  FIGS. 4-5 ; 
     Multiple springs mounted in multiple single grooves of any of the designs in Tables 1a-1g, Tables 2a-2g and in  FIGS. 1-18   f  with either radial or axial springs that can be mounted radially or axially with springs for variable force retention, play or no play and conductivity. See  FIGS. 8 and 9 . 
     Threaded grooves using a spring length retained in the groove having a groove width smaller than the coil height.  FIGS. 10   a,    10   b  and  10   d;    
     Threaded grooves using a radial or turn angle spring in length using a groove having a groove width greater than the coil width (GW&gt;CW) Table 1a, row 1, column 2, row 4, column 2 and Table 1d, rows 6-9 through Table 1f, row 5 and Table 2g, row 2 and Table 2f, row 7 and  FIGS. 5 ,  6 ,  7  and  8 ; 
     Panel mounted in a housing radial or axial spring in length and the spring can be retained in the panel or the housing for axial holding, latching or locking the panel to the housing and when in a latched or locked position the panel may be axially loaded to eliminate axial play; 
     Various types of spring-ring groove mounted designs with variable means to form a ring, ranging from threading the ends, latching the ends, interfacing the ends and butting, using non-welded springs to form a ring.  FIGS. 15 ,  16 ,  17 , and  18 ; 
     Different groove configurations that affect the force parameters, depending on the position of the point load in reference to the end point of the major axis of the coil that affects the ratio of disconnect to insertion, disconnect to running force, and the disconnect forces with a radial spring; 
     A radial or axial spring whose coil width to coil height ratio is one that will require higher force at connect and disconnect due to the smaller back angle of the coil. The closer the ratio to one the higher the force required to disconnect-connect; 
     The smaller the groove width to coil height ratio, the higher forces. Reference Table 1, row 8, column 4 vs. Table 1, row 9, column 4; 
     Variation of the groove geometry by including a step groove design to control the position of the contact point relative to the end point of the centerline. Table 1f, row 9, column 2, 7, and 11; 
     Variation of the groove geometry to control the position of the point of contact and the end point of the centerline. Table 1f, rows 6-8; 
     Device with high forces created by offsetting the centerlines of the grooves as shown in Table 2a, rows 6 and 8; 
     Reversing the direction of travel in a clockwise or counterclockwise radial spring will switch from the front angle to the back angle or vice versa, thus changing the relative position of the contact point with respect to the end point of the centerline thus varying the forces. See Table 1e and Table 2e, rows 7, column 8 and row 8, column 7 comparing the position of the contact point to the end point centerline; and 
     Retention of radial spring with a dovetail type groove Table 1d and 2d, rows 6-7. 
     Although there has been hereinabove described a specific spring latching connectors radially and axially mounted in accordance with the present invention for the purpose of illustrating the manner in which the invention may be used to advantage, it should be appreciated that the invention is not limited thereto. That is, the present invention may suitably comprise, consist of, or consist essentially of the recited elements. Further, the invention illustratively disclosed herein suitably may be practiced in the absence of any element which is not specifically disclosed herein. Accordingly, any and all modifications, variations or equivalent arrangements which may occur to those skilled in the art, should be considered to be within the scope of the present invention as defined in the appended claims.