Abstract:
This invention relates to an improvement in the manner by which the direct response sealing member (valve) is opened or uncoupled by substantially reducing the required insertion force and hence reducing the work required. A fluid channel opening of the direct response valve is initiated by the insertion of a typical male quick-disconnect coupling into a typical female quick-disconnect coupling containing this new direct response valve. A new direct response valve is designed to ensure that the internal sealing member is firstly opened in a rotational manner and then secondly, if desired, in a more typical translational manner. The new sealing member is designed to be backward compatible with existing two part quick-disconnect assemblies and this facilitates a simple one part substitution to benefit from this improvement.

Description:
BACKGROUND OF THE INVENTION 
       [0001]    This invention involves a direct response valve with a sealing member component that is opened by a manner of rotation of the sealing member and then, if desired, continues to open by axial translation of the sealing member. The design functionality utilizes other commercially-available standard components; where some, although not all, components are necessary for the new design to function. In particular, two components from pre-existing commercially available designs are utilized here in order to ensure that the new direct response valve can function and are part of this system: 1) radial “seal” between the male and female coupler and, 2) “stop and lock” or “lock” which locks the male and female coupler together under full engagement of the quick-disconnect connector. 
         [0002]    Quick-disconnect couplers are in widespread use for reliably joining fluid transfer lines, gas transfer lines and pneumatic transfer lines. Generally, an automatic shut-off value is provided, commonly called a direct response valve, which incorporates an integral valve (direct response valve with a sealing member) to seal the central passageway of the coupler automatically upon uncoupling. This integral direct response valve eliminates the need for a separate shut-off valve that would have to be actuated prior to the uncoupling; the purpose of a shut-off direct response valve is to eliminate undesirable leakage. In general, quick-disconnect couplers use many variations of locking mechanisms to automatically lock the two components of the quick coupling mechanism so that the user does not have to manually hold the two parts of the coupler together while fluid flow, thus supporting practicability. The methods of locking are varied and numerable. The type of locking features of a typical quick-disconnect coupler is not of material relevance to this discussion due to the fact that any manner of locking is merely to provide practical convenience to the user. 
         [0003]    In addition, all direct response valves contain a central sealing member which is typically located in the female coupling assembly and this component can take many different shapes. The primary features of the design of the valve are: 1) that it must comprise a smaller size than the inside annular cavity of the female coupling body and, 2) that the sealing members axial sealing surface must closely match in a circumferential manner the same or similar axial shape of surfaces as the matching female coupling. This seal takes many forms and shapes and materials and can be manufactured from a separate and pliable rubber material or a hard material; although in practice, the seal is typically much more deformable than the parent female and male bodies, in order to ensure that sealing occurs. 
         [0004]    In addition, a radial seal is required that creates a seal between the outer portion of the male coupling and the inner diameter of the female body to prevent fluid communication out of the assembly, which is commonly referred to as a “leak”. Also this radial seal ensures that the quick-disconnect connector functions and hence fluid flows between the female and the male coupler only and does not “leak” out of the coupler. 
         [0005]    In the past, a number of quick-disconnect couplings utilize a direct response valve, whereby the sealing member is caused to open by the insertion of a male coupler and the resultant axial movement of the sealing member. Typically the forward surface of the male coupler (which is of uniform length in the axial direction) communicates with the raised surface of the sealing member of the direct response valve member, thus causing all parts of the sealing member to translate in a pure axially uniform manner. Hence the sealing member and the male coupler axial movement coincide in their direction and deflection amount. 
         [0006]    Prior-art direct response valves, also known as check valves, are disclosed in Applicant&#39;s previous U.S. Pat. Nos. 8,561,640 B2; 5,005,602; 4,712,575; 4,776,369; 7,334,603; 6,978,800 and 8,596,560 B2. These prior-art disclosures incorporate only a purely axially movement of the sealing member, relative to the direct response valve body (female body and/or male body), which provided a movement where all of the sealing surfaces moved the same amount, providing a uniform circumferential opening at all locations between the sealing surfaces. Since the sealing member is translating purely axially, against the resisting fluid pressure, this means that the resulting force (of insertion of the connector) will have to overcome all the resisting pressure contained within the central chambers of the female body. The present invention is unique in that it is designed to ensure that the internal sealing member is firstly opened in a rotational manner and then secondly, if desired, in a more typical axial translational manner. This invention provides distinctive human functional advantages, due to the rotation of the sealing member during opening, namely lowering the effort of insertion as compared to prior-art submissions. 
         [0007]    Prior-art check valves (direct response valves) are disclosed in Applicant&#39;s previous U.S. Pat. Nos. 6,622,205; 5,941,278; 7,533,693 and 5,117,514 which incorporate only pure rotational means of opening a valve (or check valve) and which utilize a sealing member and a fixed rotational movement with a mechanical pivot hence whose elements are distinctly different than this submission. In addition they are not pure inline direct response (check) valves, as this submission, although they may be used as a check valves in their engaged positions. 
         [0008]    Prior-art valves are disclosed in Applicant&#39;s previous U.S. Pat. Nos. 5,501,427 (251/228); 5,620,015 and 4,561,630 and all provide both sealing member physical rotation and sealing member physical translational aspects in their designs. Although all these prior-art submissions incorporate dramatically different mechanism design elements in order to facilitate these sealing members rotational and axial movements. All prior-art submissions incorporate various combinations of the following elements, in order to create the rotation and translation of their sealing member/s, including complex mechanisms, pivots, levels, cams, sliding, wheels, counter-balance, movably connected, pressure trips, lost motion, slides, latches and limit stops. The previous submissions are dramatically different than the current submission as they involve some of the above stated elements to facilitate rotation and translation. In addition Applicant U.S. Pat. No. 5,620,015 is specially designed for use as a pipe end valve only and is not considered a pure direct response valve due to the mechanisms utilized in its design. Applicant U.S. Pat. No. 5,501,427 is specifically intended as a shut-off and flow regulation valve and is not a direct response in its dis-engaged position. Lastly, Applicant U.S. Pat. No. 4,561,630 is specifically intended as an extended period shut-off valve and is not a direct response valve in its dis-engaged position. 
         [0009]    Prior-art valves are disclosed in Applicant&#39;s previous U.S. Pat. No. 8,348,661 which incorporates true rotation of the sealing member about its longitudinal shaft axis only and no rotation of the sealing member occurs, as does in this submission. 
       BRIEF SUMMARY OF THE INVENTION 
       [0010]    This invention relates to an improvement in the manner in which the direct response valve member is opened or uncoupled by substantially reducing the required insertion force (during simple insertion) and hence reducing the work of insertion. This is accomplished by ensuring that fluid communication can occur between the two couplings (male and female couplings) or the two quick-disconnect couplings, so as to substantially improve the ease of the insertion of the coupling. 
         [0011]    This new direct response valve includes features which ensure that the sealing member is firstly movably opened in a rotational manner, then secondly in a more typical axial manner. A fluid channel opening of the direct response valve is initiated by the insertion of a typical male quick-disconnect coupling into the female quick-disconnect coupling. This female quick-disconnect coupling contains a typical direct response valve (sealing member) which incorporates features that ensure the sealing member initially opens in a rotational manner. At the outset, an axial seal exists between the sealing member and the female body. The initial fluid channel opening between the female body of the quick-disconnect valve and typical direct response valve first occurs at a singular circumferential location which initiates fluid communication between the central chambers of the male and female couplings. As the male coupling is inserted further, the fluid opening extends past a singular circumferential location and the direct response valve sealing member continues to rotate further as the male coupling is inserted. Lastly, the sealing member is translated in an axial direction, although the structure remains rotated to further open and improve fluid communication. If desired, the male and female coupling can be, if desired, held together in the final position by the use of any commercially existing locking mechanisms. The seal between the direct response valve and the female coupling can also be provided by commercially existing means such as flexible materials, ‘o’ rings, precision machining or any other desired methods. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0012]      FIG. 1  is a block view in partial section of an existing typical quick-disconnect incorporating: typical male and typical female couplers, a typical integrated direct response valve and typical fluid transmission hoses (tubes, pipes). This is a block diagram of the typical existing design which is included for comparison purposes. The valve is depicted in its closed position. 
           [0013]      FIG. 2  is an external orthographic block view of a typical quick-disconnect coupling as in  FIG. 1  which details the typical block sections. This block external view of a typical quick-disconnect coupling also shares the typical hoses (tubes, pipes). Both the existing designs and the new design of block quick-disconnect couplings look similar from an external perspective.  FIGS. 1 and 2  are included for comparison purposes. 
           [0014]      FIG. 3  is a half-section blow-up view taken along line  1 - 1  of  FIG. 2 . This is a detailed diagram of an existing typical quick-disconnect design which is provided for comparison purposes only. 
           [0015]      FIGS. 4A ,  4 B and  4 C are the plan and side views of three of many possible physical methods to design the sealing members protruding surfaces. These three examples each incorporate an angled surface of the sealing member which is a primary feature of this new design. 
           [0016]      FIGS. 5A ,  5 B and  5 C are multiple side views of various possible shapes of the individual distinct protruding members highlighting the member&#39;s effective heights. These examples of possible geometries of protruding members are provided to demonstrate the principle of the effective heights of individual protruding members as used in the two possible designs shown in  FIGS. 4A and 4C . 
           [0017]      FIG. 6  is an exploded view in section taken along line  4 - 4  of  FIG. 9 , incorporating one of a chosen sealing member as detailed in  FIG. 4B . In  FIG. 6 , the sealing member is orientated in the position prior to any movement of the sealing member. The sealing member design of  FIG. 4B  is chosen only for simplification and ease of explanation since its geometry (cylindrical shape) is the most easily displayed. 
           [0018]      FIG. 7  is a cross sectional view taken along line  7 - 7  of  FIG. 6 . The purpose of this figure is to depict sealing surfaces in plan view. The sealing member is removed from this diagram to provide clarity. 
           [0019]      FIGS. 8A ,  8 B and  8 C are sectional views along line  7 - 7  (similar to  FIG. 6 ) showing the male coupler at different stages of engagement.  FIG. 8A  is a depiction of the new quick-disconnect coupler in its first contact stage; at this stage the valve is in its closed position.  FIG. 8B  is a depiction of the new quick-disconnect coupler in full contact after complete rotation of the sealing member; at this stage the valve is in its initially-opened position.  FIG. 8C  is a depiction of the new quick-disconnect coupler in the final fully engaged stage; at this stage the valve is in its fully-opened position. 
           [0020]      FIG. 9  is an external orthographic block view of the new quick-disconnect coupling which is detailed in  FIGS. 6 ,  8 A,  8 B and  8 C. This is a block external view of the new existing design with the typical hoses (tubes, pipes). Both the existing design and the new design of block quick-disconnect couplings look similar from an external perspective. 
       
    
    
     DETAILED DESCRIPTION OF DRAWINGS 
       [0021]      FIG. 1  is a block view in partial section of a typical quick-disconnect coupling a typical existing connector allowing fluid communication that incorporates an integrated direct response valve with a sealing member. The position and the style or type of the exact sealing member shown is insignificant and  FIG. 1  is simply displayed for comparison purposes only.  FIG. 1  does not show or represent the required elements of the invention claimed; rather it is included as a block diagram representation which will provide a basis and framework for more detailed elaboration.  FIG. 1  also outlines the interfaces between typically utilized fluid transmission hoses (tubes, pipes) that are connected to both ends of the exiting typical quick-disconnect assemblies. The direct response valve is depicted in its closed position. 
         [0022]      FIG. 2  is another block view section of a typical quick-disconnect coupling (as in  FIG. 1 ) but is represented here-in although in pictorial (orthographic) view in order to further detail sectional views and block components. 
         [0023]      FIG. 3  is a sectional view taken along line  1 - 1  of  FIG. 2 . For ease of display, an existing typical direct response valve is shown here so that common surfaces can be easily shown. The sectional views shown in  FIG. 3  also do not incorporate the new required details of the invention that we are making claim to since  FIG. 3  details existing designs.  FIG. 3  does contain other components of a typical direct response valve, therefore proving the basis (starting point) upon which modifications to the typical sealing member of the direct response valve are imposed for the invention described heir-in. The direct response valve is depicted in its closed position. 
         [0024]    A typical existing direct response valve has surface  214  and surface  216  in the same plane as each other—in parallel planes. In other words there is no intentional, or substantial, angle between surface  214  and surface  216  by design or in practice. However there may be a small unintentional angle that exists between surface  214  and surface  216  due to manufacturing deviations and tolerances of manufactured parts. In a typical existing response valve the male coupler  203  moves in direction  910  where the male coupler  203  contacts sealing member  210  at surfaces  217  and  216 , respectively. This after mentioned description assumes that part  204  is stationary although the reverse of this movement is also possible; where part  204  moves in direction  905  and  203  is stationary. The resultant movement, described above in direction  910  or direction  905 , both result in surface  214  and surface  215  no longer being in contact with each other and hence the fluid seal is broken. This resultant seal break (between surface  214  and surface  215 ) results in a communication of fluid between internal central chambers  580  and  570 . This communication of fluid continues to improve as the physical opening between surface  215  and surface  214  are moved relatively further apart as the quick-disconnect connector is further engaged by independent movement in direction  910  or direction  905 . In the existing typical designs, since there is no angle between surfaces  214  and  216  (on parallel planes), the typical response valve (sealing member)  210  moves only in a linear manner in direction  910  or direction  905 , therefore there is no intentional or meaningful rotation of  210  relative to  203  or  204  (or axis  100 ) during the opening process. Since there is no rotation in the typical design, the force required to move  210  against the internal pressure in central chamber  580  (which typically exists due to the contained pressurized fluid) can be calculated as follows: quotient of the size of the area (surface  590  in compatible area units) multiplied by the internal pressure (in compatible pressure units) that exists in central chamber  580 . The pressure in central chamber  570  is assumed to be a low value approaching atmospheric pressure and is therefore considered negligible. 
       DETAILED DESCRIPTION OF THE INVENTION 
       [0025]    A direct response valve is designed to ensure that the internal sealing member is firstly opened in a rotational manner and then secondly, if desired, in a more typical axial translational manner. Following the initial rotational phase, the sealing member is now translated in an axial direction (although remains rotated) which further opens flow channels, improving fluid communication. 
         [0026]      FIGS. 4A ,  4 B and  4 C are three examples of different designs of sealing member&#39;s protrusions that would serve to ensure that the contact surfaces define a distinct and intentional angle between the sealing member&#39;s contact surfaces and the sealing surfaces. The design of this distinct and intentional angle ensures that the sealing member firstly rotates during the valve opening sequence. 
         [0027]    Note that this paragraph is identical to the previous paragraph although the details of various possible designs have been added in brackets.  FIGS. 4A through 4C  are three examples of different designs of sealing member&#39;s protrusions (protrusions are: groups  270  thru  273 , a singular  288 , and groups  274  thru  276 , respectively) that would serve to ensure that the contact surfaces (contact surfaces are: surface  292 , surface  277  and surface  291 , respectively) define a distinct and intentional angle between sealing members contact surfaces (contact surfaces are: surface  292 , surface  277  and surface  291 , respectively) and the sealing surfaces (sealing surfaces are: surface  279 , surface  278  and surface  285 , respectively). This distinct and intentional angle (Theta1, Theta2 and Theta3), by design, ensures that the sealing member firstly rotates during the valve opening sequence. 
         [0028]      FIGS. 4A ,  4 B and  4 C are three examples of sealing members that ensure this rotation occurs by design and are detailed below. There are also other designs of protrusions (a feature of the sealing member; see  FIGS. 5A ,  5 B and  5 C) that would ensure this desired initial rotation occurs followed by linear translation (if desired) along axis  100 . As depicted in  FIG. 8 , if sufficient area is exposed by rotation to separate surface  330  and surface  278 , allowing for sufficient fluid or gas flow, then the second purely linear translation (along axis  100 ) may be not required. Please note that the secondary linear translation of the sealing member is also unique in that the sealing member  288  is already rotated (unlike typical sealing members) and is then translated linearly in a rotated position along axis  100 . 
         [0029]      FIG. 4A  is the plan and side view of a possible design of the invention that depicts one physical method of designing the sealing member&#39;s part  261 . This potential design incorporates four distinct and separate protrusions, namely  270 ,  271 ,  272  and  273 . The four collective ends of four protruding surfaces (a system) define a flat plane, or the surface  292 . This surface  292  is at a distinct angle Theta1 relative to surface  279 . A design may also incorporate less than four protruding surfaces as shown in  FIG. 4C  whereby three surfaces are utilized. Also, more than four protruding surfaces may be incorporated into the design, although no design considerations above three or four protruding surfaces provide any practical advantages since a surface can be uniquely defined by the location of three points in space. 
         [0030]      FIG. 4B  is the plan and side view of another design that represents one other physical method to design sealing member  288 . This design, as detailed in  FIG. 4B , does not have distinct and separable protrusions as do the designs shown in  FIGS. 4A and 4C . The design of sealing member  288  incorporates a singular protruding cylindrical shape with interior surface  306  and exterior surface  308  with the cylindrical shape being attached at one end to surface  278 . 
         [0031]    As depicted in  FIG. 4B , this second design of sealing member  288  also incorporates a number of round shaped holes  260 , although the shape of the holes is not restricted to round-shaped holes only. Holes  260  of any shape can be utilized as long as the resultant total area of all holes is sufficient to allow desired fluid flow quantities. The holes  260  are required since the shape is cylindrical (unlike the other two designs in  FIGS. 4A and 4C ). By its nature, this cylindrical shape would prevent fluid flow without any type of holes. The interior surface  306  of the protruding cylinder is defined by the interior diameter  224  and the outer surface  308  is defined by the exterior diameter  223 . This protruding cylinder (diameter  223  and  224 ) may also take an irregular or non-cylindrical shape, although it must also incorporate the required  260  holes and the alternative shape must also not interfere as described within this paragraph. The surface  308  must not interfere during operation with the interior surface  305 , as the sealing member rotates and/or translates during operation. Similarly, surface  304  must not interfere with the cavity&#39;s interior diameter  560  as defined by surface  301 , as the sealing member rotates and/or translates during operation. These interference requirements are also applicable for all designs depicted by  FIG. 4A  and  FIG. 4C  where the external radial surfaces of the protrusions (as a system) are the elements which must not interfere with surface  305 . 
         [0032]      FIG. 4C  is the plan and side view of yet another design (third possibility) that represents one physical method to design sealing member&#39;s  262  protruding surfaces. The protruding surfaces, which are required in this design, incorporate three distinct and separate protrusions, specifically  274 ,  275  and  276 . The three collective ends of these protruding members (which form a system) define a flat plane  291  (or surface  291 ). This surface  291  is at a distinct angle Theta3 relative to surface  285 . 
         [0033]    In concept, an alternative design could also incorporate only two protruding surfaces, located circumferentially about 180 degrees from each other (around axis  100 ) to provide a high point (similar to  251   b  of design in  FIG. 4B ) and a low point (similar to  250   b  of design in  FIG. 4B ); however this design may be unstable in practice, because the fluid and/or gas flow may rock or pulsate the sealing member thus making the physical design unstable. This design does incorporate the three required points needed to define a plane, although two of these points are located on the same protruding member (since these two points are in very close proximity to each other) which results in a poor (unstable or unreliable) physical plane definition. 
         [0034]    A general statement which relates to all designs (refers to all designs discussed heir in and all other designs which meet the intention of this application) is made in the following paragraph. This general statement will be described using the design as depicted in  FIG. 4B  for ease of explanation, within the corresponding figure labels included in square brackets for the other two possible designs. Format is as follows: “ FIG. 4B  labels [ FIG. 4A  labels;  FIG. 4C  labels]”. 
         [0035]    Surface  282  [ 290 ;  286 ] can be parallel to plane  278  [ 279 ;  285 ] which is typically the case the practical design for manufacturing considerations. This new design does not define or rely on these two surfaces (i.e.  282  [ 290 ;  286 ] and  278  [ 279 ;  285 ]) being on parallel planes. In fact, surface  282  [ 290 ;  286 ] can take any physically practical shape required within the following stated limitations. Both surfaces  304  [ 280 ;  294 ] and surface  282  [ 290 ;  286 ] must not interfere with interior surface  301  as the sealing member  288  [ 261 ;  262 ] rotates and translates in operation. Surface  308  [exterior outermost radial surfaces of protrusions  270  thru  273 ; exterior outermost radial surfaces of protrusions  274  through  276 ] must not interfere with interior surface  305  as the sealing member  288  [ 261 ;  262 ] rotates and/or translates in operation. Either exterior surface  308  [external outermost surfaces of protrusions  270  thru  273 ; external outermost surfaces of protrusions  274  thru  276 ] or exterior surface  304  [ 280 ;  294 ] can serve to centre (interfere) sealing member  288  [ 261 ;  262 ] against surfaces  305  [ 305 ;  305 ] and  301  [ 301 ;  301 ] of part  401 , respectively. In addition the surfaces or seals present between surface  278  [ 279 ;  285 ] and mating surface  330  [ 330 ;  330 ] can also incorporate physical characteristics that centre part  288  [ 261 ;  262 ] in its desired location relative to the axis  100 . However, any form of centering action (interference) cannot impede the desired rotation and translation of  288  [ 261 ;  262 ] during operation as described earlier. 
         [0036]    The detailed design of the seal between surface  278  [surface  279 ; surface  330  ] and surface  330  [ 330 ;  330 ] of  FIG. 6  are not considered part of this invention, and as such are shown in a non-detailed and pictorial fashion only; they must simply seal by any manner desired. The seal between surface  278  and surface  330  could be provided by one of any standard “o” ring design or flat pliable seal design or simply a seal which relies on conforming materials or precision machining or other methods. 
         [0037]    The functioning designs must incorporate one high point (as in example  251   b  [ 251   a;    251   c ]) and one low point (as in example  250   b  [ 250   a;    250   c ]) which in turn defines Theta2 [Theta1; Theta3] angle as depicted in  FIG. 4B  [ FIG. 4A ;  FIG. 4C ]. The location circumferential of the high and low point relative to the body  401  and  400  is not critical, although the high and low points should be located approximately 180 degrees from each other (approximately across from each other though axis  100 ). This is to ensure a rotating motion and creation of an angle Theta2 [Theta1; Theta3]. Although, in theory, there could be more than one high point (as in example  251   b  [ 251   a;    251   c ]) and more than one low point (as in example  250   b  [ 250   a;    250   c ]) some of these additional points may be redundant (no contact) and redundant points will not improve the function of rotating  288  [ 261 ;  262 ]. Of less significant importance is that these additional high and low points (more than one point) may also hamper the consistent and predictable rotation of  288  [ 261 ;  262 ]. 
         [0038]      FIG. 5A  is the side view of one possible shape of the individual and distinct protruding members which may be incorporated into this design. Examples with distinct protruding members are shown in  FIGS. 4A and 4C  in order to demonstrate that the protruding members can take various shapes, with one possibility being  254  as shown in  FIG. 5A .  FIG. 5A  also shows the effective height of this protruding member  254  as being height (or length)  253 . One end of protruding members  254  is solidly connected to and is an integral part of the base  214 . Surfaces  279  and  285  ( FIGS. 4A and 4C , respectively) in the detailed designs of sealing members are in fact the same surface of the common base surface  214  as shown in  FIGS. 5A ,  5 B and  5 C.  FIG. 5B  is another possible shape of the protruding member as is  FIG. 5C . These three examples ( FIGS. 5A ,  5 B and  5 C) indicate that the effective heights  253  of all three protruding members are shown as having the same height regardless of their shape or apparent top surface details. This demonstrates that the effective heights of all protruding members as shown in  FIGS. 4A ,  4 C,  5 A,  5 B and  5 C are defined by the high point of any part of the free end (opposite of base  214  connected end) of the protruding members. This statement is generally true irrespective of the design angle Theta 1, Theta 2 and Theta3. The highest and lowest points of protruding members of the group (of quantity three to four) therefore define the rotation angle (Theta1, Theta2, Theta3) of the sealing member ( 261 ,  288 ,  262 ) as shown in  FIGS. 4A ,  4 B and  4 C. This submission aims to incorporate the variability of all designs of protruding members (as seen in  FIGS. 4A ,  4 B and  4 C) and the variability of the general shape of the individual members (if design  FIG. 4B  design is not utilized) so that the description heir in describes the defining or significant characteristics of these components as they relate to the overall functioning of this invention. 
         [0039]      FIG. 6  is an enlarged cross-sectional view of the new design incorporating one of the possible sealing members  288  (as shown in  FIG. 4B ) in an assembly which is shown in orientation prior to any contact or movement of the active components. The sealing member  288  is utilized (from  FIG. 4B ) and is incorporated in  FIG. 6  only for purposes of ease of explanation as its geometry is most simple to display. The view in  FIG. 6  is a cross-sectional plane  4 - 4  taken from  FIG. 9  depicting the new components, including: male coupler  400 , female coupler  401 , sealing member  288  and a figurative depiction of both required seals  420  (and optional stop  430  and lock  430 ). As shown in  FIG. 6 , the sealing surface  278  (see  FIG. 4B ) of sealing member  288  is in direct contact with sealing surface  330  (see  FIG. 8B ). The resultant contact of surfaces  330  (one surface of female coupler body  401 ) and surface  278  (a surface of sealing member  288 ) provide the seal between the two components of sealing member  288  and female coupler body  401 . In the orientation of components as shown in  FIG. 6 , the fluid pressure that exists within the  560  central chamber (cavity) as shown in  FIG. 6  is physically contained by surfaces  301 ,  282 ,  304  and  330  (between surfaces  330  and  278 ) and all of the surfaces of the typical hose  202  (tubes, pipes) (as shown in  FIG. 2 ). The pressure in central chamber  550  is assumed to be a low value approaching atmospheric pressure and is therefore considered negligible. 
         [0040]    The resultant pressure in the central chamber  560  (cavity) causes movement of part  288  (in the direction  905 ) against part  401  and therefore, surfaces  330  and surface  278  touch (interfere) and provide a seal. Again, the actual physical design of the seal can utilize a variety of commercially-available options although for simplicity of explanation and illustrations,  FIGS. 6 ,  7  and  8  are depicted since they are the simplest to display (i.e. seals between two simple and compliant surfaces). 
         [0041]    The sealing surfaces are shown in  FIG. 7 , which is a cross-sectional view taken along line  7 - 7  of  FIG. 6 . This figure shows that the sealing area (sealing surface only) is defined by the area that is formed between: (1) larger circle (dotted) created as the extent of surface  304  as projected onto the lip of part  401  which is surface  330 , and (2) the smaller circle defined by the smallest circle shown in  FIG. 7  which is the side view of surface  305 . These surfaces  305  and  304  are shown in  FIG. 7  as circular which is one of the typical and practical shapes that these surfaces may take, although are not limited to only perfectly circular shapes in concept. 
         [0042]      FIGS. 8A ,  8 B and  8 C are sectional views of the invention at various stages of functioning and male coupler engagement.  FIG. 6  displays the male coupler  400  in its pre-contact view.  FIG. 8A  displays the male coupler  400  in its initial first contact stage and the direct response valve is in its closed position.  FIG. 8B  shows the male coupler  400  in its highest surface contact and complete rotation of sealing member  288  stage; at this stage the direct response valve is at its initially-opened position.  FIG. 8C  displays the male coupler  400  in its final and fully engaged stage of operation; at this stage the valve is in its fully-opened position. In  FIG. 8A  through  FIG. 8C , only the male coupler  400  and sealing member  288  move in direction  910  and rotation  430 , while the female coupler  401  remains stationary. [See former description of the opposite form of engagement in which male coupler  400  is stationary and female coupler  401  moves in direction  905  and  288  moves in direction  905  and also rotates in direction  430 . This opposite direction of movement still provides the same opening of sealing member  288  although this movement is not depicted in any figures. 
         [0043]      FIG. 8A  shows male coupler  400  in its initial first contact stage as the male coupler starts movement in direction  910  along axis  100 . Male coupler  400  makes initial contact with sealing member  288  at the high point  251   b  of sealing member  288 . The male coupler  400  continues to move in direction  910  along axis  100  past the orientation as shown in  FIG. 8A . This causes translation of the sealing member in direction  910  and rotation of the sealing member  288  in direction  430  due to the angled surface (Theta 2) of the sealing member  288  (relative to surface  340  of part  400 ). This rotation of part  288  in direction  430  is centred approximately around a rotation point  402 , as detailed in the blow up of  FIG. 8B . Point  402  is located approximately at the outmost edge (top left hand corner) of part  288  (as orientated in all  FIG. 8 ) in which the outer edge of part  288  (circular line where surfaces  278  and surface  304  meet) touches surface  330  as detailed in the blow-up of  FIG. 8B . The exact rotation point is physically dependent on the style of the particular seal used, although the rotation in direction  430  of sealing member  288  will generally occur around the same region of point  402 . In typical use, there exists a pressure in the interior cavity  560 , which is created by contained fluid. In turn, this pressure causes a force onto part  288  as exerted in direction  905  (assuming part  401  is stationary) from application of the internal pressure in central chambers  560  on surface  282 . The force on part  288  in direction  905  causes a transfer of force at high point  251 d from part  288  to part  400 . This contact occurs since part  400  is moving in the direction  910  and part  288  is moving in the opposite direction  905 . This resistance force, which is a result of the insertion of part  400 , increases as the movement of part  400  in direction  910  continues. At a specific angle not explicitly depicted in figures (Theta 12; where Theta 12 is less than Theta10) the seal breaks and fluid communication occurs between central chambers  560  and  550 . This angle (Theta 12) is entirely dependent on the style and materials used in the specific seal design and on the physical geometry of the sealing member. Regardless of the seal design that is incorporated, the description heir in remains valid and the fluid communication simply starts at a unique and repeatable angle (the specific angle is unique to seal design and materials chosen which in turn determines the unique Theta 12). Once the seal breaks, the resistance force of insertion reduces due to the flow of fluid out of central chamber  560 . Part  288  thus continues to rotate in direction  430  until it reaches the orientation shown in  FIG. 8B  where part  288  has rotated to its maximum Theta 10 (angle extent) and surface  277  (of part  288 ) is now coincident with surface  340  (of part  400 ).  FIG. 8B  also demonstrates that the rotation point of part  288 ,  402 , is still in contact with surface  330 . Since there remains contact between part  288  and part  401  (at the rotation point  402 ), the force of insertion of part  400  from the breaking of seal position to this position remains less than all standard and typical existing designs as depicted in  FIG. 3 . The insertion force required is less than existing designs because surface  330  continues to react (resist or supports in direction  910 ) some of the force exerted on part  288  in direction  905  (from internal pressure within central chamber  560 ) which results in less insertion force being required on part  400  in the direction  910 . 
         [0044]    As shown in  FIG. 8B , because part  288  is in direct contact with part  400 , any further linear movement of part  400  due to continued insertion of  400  in direction  910  results in both parts  400  and  288  now moving in tandem in the direction  910  along axis  100 . No further rotation of part  288  occurs. There continues to be fluid communication between central chamber  560  and central chamber  550 . The desired fluid communication occurs from central chamber  560  through the gap (opening between surfaces) created between surfaces  330  and  278  subsequently this occurs through the internal holes  260  which exist in part  288 , and out of the central chamber of part  288  and finally into central chamber  550 . This continued fluid or gas flow continues to further reduce the resistant force of insertion of part  400  in direction  910 . As depicted in  FIG. 8C , depending on the commercially available design utilized for the locking mechanism  430  (and physical stop  430 ) the linear motion of parts  400  and rotated part  288  in direction  910  (at constant angle Theta 11) ceases.  FIG. 8C  also displays the final stage of engagement, which is when the physical stop  430  (and locking mechanism  430 ) also stop further insertion (resists further motion of  400  in direction  910 ). The locking mechanism  430  also typically includes a physical stop  430  and are only discussed since both features are typical in all practical quick-disconnect assemblies although neither are considered unique features of this new design. Lock  430  and stop  430  are included for discussion only because they do provide convenience to the user. 
         [0045]    The sum of the total force (F) of insertion (force on part  400  as it is inserted) through the total distance (d) of travel distance  410  and hence the total work (W), of insertion, required (W=F×d) for this new design is considerably less than existing prior-art designs. The exact reduction in force achieved when modifying a particular existing design (modifying old sealing member to the new sealing member design and possible modifications of associated supporting parts) can easily be confirmed by lab experiments and/or simulations. 
         [0046]    Since the connector insertion force is usually exerted by a human, and since all humans have maximum physical force limitations and total work output limitations, the improvement offered by this invention provides dramatic improvement in consumer usability. This new design is particularity of benefit in fluid systems which utilize higher pressure fluid or gas levels. High fluid or gas pressure levels exist in most residential pressured water systems and in most commercial water, fluid or gas delivery systems. 
         [0047]    In this specification have been described, including a number of particular mechanical arrangements of the protruding members, sealing member and seals; it will be understood that other forms, which operate in the same manner as that described, can be readily utilized in this invention. 
         [0048]    In addition, it is understood that whilst the invented valve is particularly useful in quick-disconnect assemblies operated by humans that its benefits are also applicable in uses of automation such as robots and other automation. 
         [0049]    All such modifications and applications are deemed to be within the spirit and scope of the invention. 
         [0050]    Any references in this invention to the term “liquid” or “fluid” are to be analogous and replaceable with any known liquid or gas material which behaves as a liquid or gas which includes and is not limited to water, fluids, all liquids, all gases, compressed gases, ngl, cng, Ng, slurries and gels. 
         [0051]    Utilizing a standard cylindrical coordinate system with axial [typical Z direction], radial [typical Euclidean radial distance from Z axis] and circumferential [angular] directions; where the axial direction coincides with the upstream direction  910  and the downstream direction  905 ; the axis of the axial direction is depicted as line  100  on  FIGS. 3 ,  6 ,  8 A,  8 B and  8 C; where the radius [R] has a magnitude of zero at the axial [Z] axis  100 ; hence the resulting circumferential direction coincides with the standard circumferential direction of the coordinate system.