Patent Description:
Breakaway connectors or assemblies can be utilized in fluid dispensing systems, such as refueling stations and the like. The breakaway assemblies are designed to provide a break in the fluid system which can be closed when a sufficient, predefined separation force is applied thereto. For example, in a drive-away event, the user of a refueling unit may inadvertently leave the nozzle in the tank of a vehicle or automobile and drive away. Breakaway assemblies are designed to provide a breakaway point at which the hose or system can be separated, and also provide a closing valve to prevent or minimize loss of fuel. However, many current breakaway assemblies have various drawbacks.

Single use breakaways typically use shear pins or shear grooves, but such shear elements cannot be fully tested during assembly, which can lead to unpredictable performance. Many existing reconnectable breakaways use using garter springs, canted coil springs, compression springs and deflectable members to provide a releasable connection mechanism. However such releasable connection mechanisms can have relatively high variances in the materials and/or tolerances, and thus lead to unpredictable separation force.

Existing breakaways can also have issues accommodating pressure pulses in the dispensed fluid. Since single use breakaways use a rigid member that is designed to shear or break when sufficient force is applied, and such components can undesirably separate when a sufficiently powerful pressure pulse is transmitted. Reconnectable breakaways can also be prone to separation due to force or pressure spikes and/or internal components can be damaged due to the force or pressure spike.

Finally, existing breakaways typically have valves that are designed to close after a breakaway event. However the valves may not close in a sufficiently predictable manner.

<CIT> discloses a breakaway coupling utilizing a continuous metallic annulus with a metal base and a spacer that holds a series of standard round magnets equally spaced around the approximate perimeter of the spacer and its base.

The present invention provides a breakaway assembly that is reconnectable, provides a relatively consistent separation force, using magnets, in one case which can accommodate force or pressure spikes, and in one case provides an improved closure valve arrangement. More particularly, in a first aspect, the invention provides a breakaway assembly comprising a first connector and a second connector releasably coupleable to said first connector, wherein said assembly is movable between a first configuration in which said first and second connectors are releasably coupled and together define a fluid path through which fluid is flowable, and a second configuration in which said first and second connectors are not coupled together, wherein said assembly is configured to move from said first configuration to said second configuration when a predetermined separation force is applied to the assembly. The assembly includes a closure valve positioned in one of said first or second connectors, wherein said closure valve is configured to be in an open position when said assembly is in said first configuration to allow fluid to flow therethrough, and to move to a closed position when the assembly moves to said second configuration to generally block the flow of fluid therethrough. The assembly includes an attraction member coupled to one of the first or second connectors, and a magnet unit coupled to the other one of the first or second connectors, wherein the attraction member and the magnet unit are magnetically attracted to each other when the assembly is in the first configuration to retain assembly in the first configuration, wherein the magnet unit includes a channel or channels that includes a plurality of magnets or a magnet received therein, wherein the magnets are positioned at an angle other than perpendicular relative to a radial line of the breakaway assembly in axial end view, and wherein a face corresponding to a pole of each magnet lies in a plane oriented parallel to a central axis of the assembly.

A second aspect of the present invention provides a method for using breakaway assembly comprising: accessing a breakaway assembly including a first connector and a second connector releasably coupleable to said first connector, wherein said assembly is movable between a first configuration in which said first and second connectors are releasably coupled and together define a fluid path through which fluid is flowable, and a second configuration in which said first and second connectors are not coupled together, wherein said assembly is configured to move from said first configuration to said second configuration when a predetermined separation force is applied to said assembly, the assembly including a closure valve positioned in one of said first or second connectors, wherein said closure valve is configured to be in an open position when said assembly is in said first configuration to allow fluid to flow therethrough, and to move to a closed position when said assembly moves to said second configuration to generally block the flow of fluid therethrough, the assembly further including an attraction member coupled to one of the first or second connectors and a magnet unit coupled to the other one of the first or second connectors, wherein the attraction member and the magnet unit are magnetically attracted to each other when the assembly is in the first configuration to retain the assembly in the first configuration, wherein the magnet unit includes a channel that includes a plurality of magnets received therein, wherein the magnets are positioned at an angle other than perpendicular relative to a radial line of the breakaway assembly in axial end view, and wherein a face corresponding to a pole of each magnet is lies in a plane oriented perpendicular parallel to a central axis of the assembly; and releasably coupling the first and second connectors together such that the assembly is in the first configuration.

<FIG> is a schematic representation of a refilling system <NUM> including a plurality of dispensers <NUM>. Each dispenser <NUM> includes a dispenser body <NUM>, a hose <NUM> coupled to the dispenser body <NUM>, and a nozzle <NUM> positioned at the distal end of the hose <NUM>. Each hose <NUM> may be generally flexible and pliable to allow the hose <NUM> and nozzle <NUM> to be positioned in a convenient refilling position as desired by the user/operator.

Each dispenser <NUM> is in fluid communication with a fuel/fluid storage tank <NUM> via a liquid or fluid conduit or path <NUM> that extends from each dispenser <NUM> to the storage tank <NUM>. The storage tank <NUM> includes or is fluidly coupled to a fuel pump <NUM> which is configured to draw fluid/fuel out of the storage tank <NUM> via a pipe <NUM>. During refilling, as shown by the in-use dispenser <NUM>' of <FIG>, the nozzle <NUM> is inserted into a fill pipe <NUM> of a vehicle fuel tank <NUM>. The fuel pump <NUM> is then activated to pump fuel from the storage tank <NUM> to the fluid conduit <NUM>, hose <NUM> and nozzle <NUM> and into the vehicle fuel tank <NUM> via a fuel or fluid path or fluid conduit <NUM> of the system <NUM>.

In some cases, the system <NUM> may also include a vapor path <NUM> extending from the nozzle <NUM>, through the hose <NUM> and a vapor conduit <NUM> to the ullage space of the tank <NUM>. For example, as shown in <FIG>, in one embodiment the vapor path <NUM> of the hose <NUM> is received in, and generally coaxial with, an outer fluid path <NUM> of the hose <NUM>. The nozzle <NUM> may include a flexible vapor boot or bellows, sleeve or the like (not shown) of the type well known in the art which is coupled to, and circumferentially extends around, a spout <NUM> of the nozzle <NUM>.

The bellows is designed to form a seal about the spout <NUM> when the spout <NUM> is inserted into the fill pipe <NUM>. The bellows help to capture vapors and route the vapors into the vapor path <NUM>, although vapors can also be captured with nozzles <NUM> lacking a bellows. The system <NUM> may include a vapor recovery pump <NUM> which applies a suction force to the vapor path <NUM> to aid in vapor recovery, although in some cases (e.g. so-called "balance" systems) the vapor recovery pump <NUM> may be omitted. In addition, in some cases the system <NUM> may lack the vapor path <NUM>, in which case the system <NUM> may lack the vapor conduit <NUM>, and the hose <NUM> may lack the vapor path <NUM> therein.

The system <NUM> disclosed herein can be utilized to store/dispense any of a wide variety of fluids, liquids or fuels, including but not limited to petroleum-based fuels, such as gasoline, diesel, natural gas (including compressed natural gas (CNG)), biofuels, blended fuels, propane or liquefied petroleum gas (LPG), oil or the like, or other fuels or liquids such as hydrogen, ethanol and the like.

Each dispenser <NUM> may include a breakaway assembly <NUM> associated therewith, which can be located at various positions on the dispenser <NUM>, or along the system <NUM>. For example, the left-most dispenser <NUM>' of <FIG> utilizes a breakaway assembly <NUM> at the base end of the hose <NUM>; the middle dispenser <NUM> of <FIG> utilizes a breakaway assembly <NUM> positioned adjacent to the nozzle <NUM>; and the right-most dispenser <NUM> of <FIG> utilizes a breakaway assembly or assembly <NUM> at an intermediate position of the hose <NUM>. However, it should be understood that the breakaway assembly <NUM> can be positioned at any of a wide variety of positions along the length of the hose <NUM>, or at other positions in the refueling system <NUM>. The breakaway assembly <NUM> may include, and/or be coupled to, a swivel assembly to enable the breakaway assembly <NUM> to assume various positions and become aligned with any separation forces applied thereto.

<FIG> and <FIG> illustrate one embodiment of the breakaway assembly <NUM>, for use with conventional (typically liquid) fuels such as gasoline, diesel, oil or the like that are pumped under relatively low pressure, such as less than about <NUM> MPa (<NUM> psi) in one case, or less than about <NUM> MPa (<NUM> psi) in another case, or less than about <NUM> MPa (<NUM> psi) in another case, or less than about <NUM>. 068MPa (<NUM> psi) in yet another case. The breakaway assembly <NUM> includes a first or upstream connector <NUM> releasably connected to a second or downstream connector <NUM>. The breakaway assembly <NUM> and connectors <NUM>, <NUM>, are generally annular in one case, with the fluid path <NUM> positioned therein, but can have other shapes as desired. The first connector <NUM> may be connected to an upstream portion of the system <NUM>/hose <NUM>, and the second connector <NUM> may be connected to a downstream portion of the system <NUM>/hose <NUM> (it should be understood that terms used in relation to the direction of flow, such as "upstream" and "downstream," are used herein with respect to the direction of the flow of fluids/fuel to be dispersed (i.e. right-to-left in <FIG>, <FIG>, <FIG> and14, and left-to-right in <FIG>, as opposed to for example the direction of vapor flow, unless specified otherwise). However, if desired this orientation may be reversed such that first connector <NUM> is connected to a downstream component, and the second connector <NUM> is connected to an upstream component. Both the first connector <NUM> and second connector <NUM> can include threaded surfaces (such as the illustrated internal threaded surfaces or threaded adapters <NUM>) for securing the connectors <NUM>, <NUM> to the associated upstream and downstream components. The threaded surfaces <NUM> could instead take the form of externally threaded surfaces, or various other coupling structures besides threaded surfaces may be used.

The first connector <NUM> may include a generally tubular or annular coupling portion <NUM>, which can have a variety of shapes in cross section, and which can be removably receivable in a socket or protective cover <NUM> of the second connector <NUM>. The second connector <NUM> further includes a closure valve or poppet valve <NUM> positioned therein. The poppet valve <NUM> includes a body portion <NUM> having a downstream stem <NUM>, an upstream stem <NUM>, and seal or sealing portion <NUM> coupled to the body portion <NUM>. The downstream stem <NUM> is slidably received in a guide <NUM> which is positioned or centered in the second connector <NUM> by a plurality of radially-extending fins <NUM>. The poppet valve <NUM> further includes a spring <NUM> positioned axially between the guide <NUM> and the body portion <NUM>. The body portion <NUM>/poppet valve <NUM> is thereby biased, by the spring <NUM>, to an upstream/closed position in which the sealing portion <NUM> sealingly engages the poppet valve seat <NUM> (see <FIG>). The second connector <NUM> may include a seal <NUM> on a radially outer surface of its axially-forwardly extending end to help form a seal with the inner surface of the first connector <NUM>.

The first connector <NUM> may include a closure valve or poppet valve <NUM> positioned therein. The poppet valve <NUM> includes a body portion <NUM> having a downstream stem <NUM>, an upstream stem <NUM>, and seal or sealing portion <NUM> coupled to the body portion <NUM>. The upstream stem <NUM> is slidably received in a guide <NUM> which is positioned/centered in the first connector <NUM> by a plurality of radially-extending fins <NUM>. The poppet valve <NUM> further includes a spring <NUM> positioned between the guide <NUM> and the body portion <NUM>. The body portion <NUM>/poppet valve <NUM> is thereby biased, by the spring <NUM>, to a downstream/closed position in which the sealing portion <NUM> sealingly engages the poppet valve seat <NUM> (see <FIG>).

During normal operation of a dispenser <NUM>, the first connector <NUM> and second connector <NUM> are arranged in their first/locked/connected/engaged state or configuration, as shown in <FIG>, in which the first <NUM> and second <NUM> connectors are coupled together and define an open fluid conduit, or fluid path <NUM> through which fluid may flow, as shown by the arrows of <FIG>. In this configuration, the upstream stem <NUM> of the poppet valve <NUM> engages and moves the downstream stem <NUM> of poppet valve <NUM> away from its valve seat <NUM>, and vice versa, such that the springs <NUM>, <NUM> of both poppet valves <NUM>, <NUM> are compressed and both poppet valves <NUM>, <NUM> are opened. When the poppet valves <NUM>, <NUM> are opened the seals <NUM>, <NUM> are spaced away from their associated seats <NUM>, <NUM>, enabling fluid to flow through the fluid path <NUM>/breakaway assembly <NUM>/connectors <NUM>, <NUM>. As will be described in greater detail below, a coupling mechanism or coupling system <NUM> is provided to releasably couple the connectors <NUM>, <NUM> in the axial direction.

When sufficient separation forces are applied to the assembly <NUM> (i.e. forces applied at least partially along the axis of the breakaway assembly <NUM>/connectors <NUM>, <NUM>), the coupling mechanism <NUM> releases/separates and the breakaway assembly <NUM> moves to its second/separated/disconnected state or configuration as shown in <FIG>. When the connectors <NUM>, <NUM> are moved away from each other, the downstream stem <NUM> of the poppet valve <NUM> is pulled away from the upstream stem <NUM> of poppet valve <NUM>. The relative movement of the connector(s) <NUM>, <NUM> away from each other enables the poppet valves <NUM>, <NUM> to move to their closed positions, as shown in <FIG> in which the seals <NUM>, <NUM> engage their associated valve seats <NUM>, <NUM>, as biased by their associated springs <NUM>, <NUM>.

The assembly <NUM> may be reusable and may be configured such that the connectors <NUM>, <NUM> are connectable/reconnectable (i.e. movable from the configuration of <FIG> to that of <FIG>) without requiring any repair or replacement of any components of the assembly <NUM>. In particular, when the first connector <NUM> and second connector <NUM> are connected/reconnected, the downstream stem <NUM> of the poppet valve <NUM> engages the upstream stem <NUM> of the poppet valve <NUM>. When sufficient axial compression forces are applied to the assembly <NUM> during the reconnection process, the body portions <NUM>, <NUM> of the poppet valves <NUM>, <NUM> and associated seals <NUM>, <NUM> are moved away from their respective valve seats <NUM>, <NUM> until the valves <NUM>, <NUM> are in the position shown in <FIG>.

The illustrated embodiment shows both the first <NUM> and second <NUM> connectors having poppet valves <NUM>, <NUM> therein. However, in an alternate embodiment, only one of the connectors <NUM>, <NUM> has a poppet valve. In this case, the other connector <NUM>, <NUM>, lacking a poppet valve, may include a rigid, axially-extending hold-open stand, analogous to the portions <NUM>/<NUM>, which extends axially forwardly and can engage the poppet valve (e.g. valve <NUM>, <NUM>) in the other connector <NUM>, <NUM> and urge the other poppet valve to the open position when the assembly <NUM> is in its connected configuration. In yet another alternate embodiment, when the assembly <NUM> is used with dispensing systems utilizing vapor recovery systems, one or both of the connectors <NUM>, <NUM> may include poppet valves in or at least partially defining the vapor path <NUM> which are opened when the assembly <NUM> is in the connected configuration, and which automatically close when the assembly <NUM> moves to the disconnected position. Examples of these arrangements are disclosed in <CIT>.

The assembly <NUM> may include the coupling mechanism <NUM> which releasably couples the connectors <NUM>, <NUM> together to retain the assembly <NUM> in its coupled position until sufficient axial forces are applied. The coupling mechanism <NUM> includes a magnet unit <NUM>, which includes a magnet coupler <NUM> that receives various magnets <NUM> therein. The magnet unit <NUM> is coupled to the first connector <NUM> in the illustrated embodiment. The coupling mechanism <NUM> includes an attraction member <NUM> (or other member which completes the magnetic circuit) which can be made of a ferrous material or other material that is magnetically attracted or attractable to the magnets <NUM>/magnet unit <NUM>. The attraction member <NUM> is coupled to the second connector <NUM> in the illustrated embodiment. In the particular illustrated embodiment the magnet unit <NUM> constitutes or defines the coupling portion <NUM> of the first connector <NUM> that is received in the socket/cover <NUM> of the second connector <NUM>. If desired, the positioning of the magnet unit <NUM> and attraction member <NUM> can be reversed from that shown such that the attraction member <NUM> is coupled to the first connector <NUM>, and the magnet unit <NUM> is coupled to the second connector <NUM>.

In one embodiment the attraction member <NUM> is generally annular and made of a ferrous material or other magnetizable material, and directly threadably attached to the body of the first connector <NUM>. The attraction member <NUM> could instead be made of or include a magnet or magnets configured and arranged to be magnetically attracted to an associated magnet(s) <NUM> of the magnet unit <NUM> when properly aligned. Further alternately, rather than being a continuous annular member, the attraction member <NUM> can instead take the form of various, discrete and spaced apart attraction member units or portions positioned to magnetically interact with the magnet unit <NUM>.

The magnets <NUM> of the magnet unit <NUM> can be made of any of a wide variety of materials, including permanently magnetized materials such as rare earth magnets, including neodymium in one case. The magnet coupler <NUM> and/or attraction member <NUM> can be made of a magnetized and/or magnetizable material such as ferromagnetic material or metal (iron, cobalt, nickel, manganese, gadolinium, dysprosium or others), paramagnetic materials, diamagnetic materials, ferrimagnet metals, ferromagnetic alloys, sheet steel or cast steel, or in some cases non-magnetized or non-magnetizable material, each of which can if desired be covered with a ferromagnetic coating or plating, such as nickel in one case but could be nearly any ferromagnetic metal or alloy which will not unduly interfere with any potentially desired magnetic field. The magnets <NUM> and/or magnet coupler <NUM> and/or attraction member <NUM> can be plated, coated, encapsulated or unplated.

In one case the magnet coupler <NUM> and/or attraction member <NUM> can have, or be made of a material having, a saturation point that is greater than about <NUM> Tesla to provide the desired ferromagnetic response. In particular, it may be desired to have the magnet coupler <NUM>, as energized/magnetized by the magnets <NUM> received therein, magnetically interact with the attraction member <NUM> as a unit, rather than have the individual magnets <NUM> directly magnetically interact with the attraction member <NUM>. The magnet coupler <NUM> can thus be configured, sized and shaped to direct the magnet field in a desired and advantageous manner. In particular, by passing the induced magnetic field through the magnet coupler <NUM>, the magnetic field lines originating with the magnets <NUM> tend to pass through the radially inner <NUM> and radially outer <NUM> annular components or surfaces of the magnet coupler <NUM> (and not, for example, through the web or end wall <NUM> at the base of the magnet coupler <NUM>), which provides a stronger magnetic force since the web <NUM> acts as a shunting member. Moreover, since the web <NUM> acts as a shunting member it may be desired to avoid or minimize the magnetic field lines passing through the web <NUM>, and thus may be desired to keep the web <NUM> as thin as possible.

The web <NUM> may have a thickness (e.g. in the axial direction) that allows the greatest amount of magnetic flux field to pass into/through the magnet coupler <NUM>, which is dependent on a balance of factors, including the strength of the magnetic field, and the permeability and saturation limits of the materials of the magnet coupler <NUM>. The ratio of the thickness of the web <NUM>, to the field penetration depth, may between about <NUM>% and about <NUM>% in one case, where the field penetration depth is dependent on the saturation point of the material of the magnet coupler <NUM>. In a case where the magnetic flux density is between <NUM> T and 2T, the field penetration depth can be between <NUM> (<NUM> inch) and <NUM> (<NUM> inch), and the thickness of the web <NUM> can range from <NUM> (<NUM> inch) to <NUM> (<NUM> inch). In one case the web <NUM> has an axial length of less than about <NUM>% in one case, or less than <NUM>% in another case, or less than <NUM>% in another case, or less than <NUM>% in another case of a length of the magnets <NUM> and/or length of the magnet unit <NUM>. In some cases it may be desired to eliminate the web <NUM> entirely for magnetic performance, but doing so could create difficulties in physically retaining the magnets <NUM> in the desired axial position in the magnet coupler <NUM>. In some cases the web <NUM> can be slotted or have other openings to reduce the shunting effect of the web <NUM>.

The attraction member <NUM> and magnet unit <NUM> can thus form the coupling mechanism <NUM> that releasably couples the connectors <NUM>, <NUM> together and tends to retain the assembly <NUM> in its first/locked/connected/engaged state or configuration, as shown in <FIG>. The coupling mechanism <NUM> may thus solely or primarily determine the separation force of the breakaway assembly <NUM>.

When an external axial force is applied to the breakaway assembly <NUM> that is greater than the attractive force of the magnet unit <NUM> to the attraction member <NUM>, a separation will occur in the following sequence. The downstream connector <NUM> will first move away from the upstream connector <NUM>, along with nearly all associated portions of the downstream connector <NUM> (e.g. except for the associated poppet valve <NUM> which may begin to close). Both poppet valves <NUM>, <NUM> may simultaneously start move to their closed position. In one case, after roughly <NUM> (<NUM>/<NUM> inch) of travel of the connectors <NUM>, <NUM> away from each other, both poppet valves <NUM>, <NUM> will be fully moved to their closed positioned. As the separation motion continues, at a greater distance, about <NUM> (<NUM>/<NUM> inch) of travel in one case, the upstream connector <NUM> will be fully extracted out of the socket <NUM> of the downstream connector <NUM> (shown as nearly fully extracted in <FIG>). In this state the connectors <NUM>, <NUM> are separated and the poppet valves <NUM>, <NUM> are closed to prevent or limit the leakage of fluid.

After the connectors <NUM>, <NUM> are separated, it may then desired to reconnect the connectors <NUM>, <NUM>. In one case the connectors <NUM>, <NUM>, can be axially aligned and manually pressed together such that the magnet unit <NUM> fits into the socket <NUM>. The connectors <NUM>, <NUM> are then pressed together, and the springs <NUM>, <NUM> compressed until the poppet valves <NUM>, <NUM> are open as shown in <FIG>. During a reconnection event, since the attraction member <NUM> is positioned on or in the downstream connector <NUM>, the magnet unit <NUM> will be at some point during insertion be sufficiently attracted to the attraction member <NUM> such that the magnet unit <NUM>/assembly <NUM> may be felt to "snap" into place. In addition, the attraction between the magnet unit <NUM> and the attraction member <NUM> may reduce the reconnection force and act as a magnetic assist feature, aiding a user in reconnection. Thus the (manual) force required to connect the first <NUM> and second <NUM> connectors can be less than the force required to separate the first <NUM> and second <NUM> connectors in a breakaway event, which can provide an easier and more convenient reconnection process.

In the embodiment shown in <FIG>, (wherein <FIG> are disclosed herein, but not part of the claimed invention, due to the particular orientation of the magnets shown therein) the magnet coupler <NUM> has an upstream portion 102a with an annular channel or channel portion <NUM> formed therein, that is removably attachable to a downstream portion 102b with a correspondingly shaped and located channel or channel portion <NUM>. Each portion 102a, 102b can have a web or end wall <NUM> positioned at an axial end of the portion 102a, 102b and positioned adjacent to the associated channel <NUM>, <NUM>. The upstream 102a and downstream 102b portions can be separate components or parts that are coupled together at or along a joint <NUM> that is aligned in a radial plane. One or both channel portions <NUM>, <NUM> can receive the magnets <NUM> therein. Each magnet coupler portions 102a, 102b can include a threaded surface <NUM> thereon, where the threaded surfaces <NUM> are configured to threadably engage each other to form the generally closed magnet coupler <NUM> shown in <FIG> (when assembled) and <FIG>. When the magnet unit <NUM> is fully assembled by joining the upstream 102a and downstream 102b portions by mechanical, releasable or other means an internal, closed channel <NUM>, <NUM> is formed therein that receives and encapsulates the magnets <NUM> therein.

In the illustrated embodiment and with reference to <FIG>, which is disclosed herein, but not part of the claimed invention, due to the particular orientation of the magnets shown therein, in one case each magnet <NUM> is shaped as a rectangular prism and the poles <NUM>, <NUM> of the magnets <NUM> are oriented perpendicular to the largest face of the magnet <NUM>. In one case the magnets <NUM> are arranged with their north poles <NUM> positioned on (extending perpendicular to) the radially inner faces of the magnets <NUM>, and their south poles <NUM> positioned on (extending perpendicular to) the radially outer faces of the magnets <NUM>. Thus the poles <NUM>, <NUM> of the magnets <NUM> can be oriented perpendicular to the central axis A (<FIG>) of the assembly <NUM>, or non-parallel with axis A, and aligned with a radial line pointing radially inwardly or outwardly.

As shown in <FIG>, which is disclosed herein, but not part of the claimed invention, due to the particular orientation of the magnets shown therein, in one case the channel <NUM> of the upstream portion 102a can be formed in end view as a prism with a number of sides (twelve sides in the illustrated embodiment) that corresponds to the number of magnets <NUM>, where the number of sides of the channel <NUM> can be adjusted to match the number of magnets <NUM> to be used. It is noted that while <FIG> illustrates the channel <NUM> formed in portion 102a, the channel <NUM> in the portion 102b can have the same shape and positioning. It is also noted that when the channels <NUM>, <NUM> are not circular, the magnet coupler portions 102a, 102b may be connected together by means other than threaded surfaces <NUM>, such as by using press fit, rabbiting, retaining rings or the like. The polygon shape for the channels <NUM>, <NUM> can help to reduce any air gap between the poles/largest face of the magnets <NUM> and the magnet coupler <NUM>, thereby increasing magnetic performance. In addition, this configuration enables the use of magnets <NUM> that are rectangular prisms, as compared to for example curved magnets, which can be more expensive and difficult to manufacture.

The polygon of the channels <NUM>, <NUM> can be regular or irregular, and in one case has at least four sides. However the polygon-shaped channel <NUM>, <NUM> can in some cases be difficult to machine. Thus if desired channels <NUM>, <NUM> having a circular shape, which is easier to machine, can be used as shown in <FIG>, (wherein <FIG> is disclosed herein, but not part of the claimed invention, due to the particular orientation of the magnets shown therein) and used in conjunction with rectangular prism magnets <NUM>. In this case the magnets <NUM> can be positioned tangent to the channel <NUM>, <NUM>. Moreover, in this case the magnets <NUM> and/or channel <NUM>, <NUM> can also be configured such that each magnet <NUM> has three points of contact (or potential contact) with the channel <NUM>, <NUM>: the center portions of each magnet <NUM> may be in contact or near contact with the radially-inner wall of the channel <NUM>, <NUM>, and the circumferentially outer portions of each magnet <NUM> may be in contact or near contact with the radially-outer wall of the channel <NUM>, <NUM>. The three points of contact (or near contact) helps to securely locate each magnet <NUM> in the channel <NUM>, <NUM>.

In order to position the magnets <NUM> in the channel <NUM>, <NUM> it may not be practical to provide three points of actual contact due to lack of sufficiently precise manufacturing and lack of sufficient tolerances. In this case there may be a relatively small radially-extending outer gap <NUM> between the circumferentially outer portions of the magnets <NUM> and the radially-outer wall of the channel <NUM>, <NUM>, and/or between the inner/central surface of the magnets <NUM> and the radially-inner wall of the channel <NUM>, <NUM>. The gap(s) <NUM> for a given magnet <NUM> may have a total cumulative length (in the radial direction) of less than about <NUM> (<NUM> inch) in one case, or less than about <NUM> (<NUM> inch) in one case, or less than about <NUM> (<NUM> inch) in another case, or less than about <NUM>% of the length of the magnet <NUM> (in a generally circumferential direction). The gap(s) <NUM> may also be less than about <NUM>% in one case, or less than about <NUM>% in another case, relative to a radius of an outer surface of the portion 102a/102b.

Each magnet <NUM> may also define a somewhat triangular-shaped gap <NUM> positioned between the circumferentially-outer portions of adjacent magnets <NUM> and the radially inner surface of the channel <NUM>, <NUM>. The inner gap <NUM> can be reduced as more magnets <NUM> are used. The gap(s) <NUM> for a given magnet <NUM> can each, or cumulatively, have a length in the radial direction that corresponds to the parameters of the gap <NUM> outlined above.

The magnets <NUM> can also be positioned in various different arrangements such as that shown in <FIG> wherein the magnets <NUM>, in end view, are positioned in discrete, spaced apart, generally radially aligned closed channels, in the same or similar manner as shown in the embodiment of <FIG>, <FIG> and <FIG> and described in greater detail below. Alternatively, as shown in <FIG> the magnets <NUM> can be positioned in channels <NUM>, <NUM> that form various angles (defined by the angle between: a) a radially outwardly extending line aligned with the channel <NUM>, <NUM> and b) a radial line, as shown by the labelled angles in <FIG>). Thus the plane defined by the largest faces of the magnets <NUM> can be oriented perpendicular to a radial line (<FIG>, both not part of the claimed invention), wherein the poles are aligned with a radial line), or parallel to radial line (<FIG>, wherein the faces corresponding to the poles are oriented parallel to a radial line) or positioned at various angles relative to a radial line (<FIG>).

Since each magnet <NUM> can be formed as a rectangular prism, each magnet <NUM> may have a longest dimension (a length, in one case), that extends or is oriented or aligned axially in the disclosed embodiment. Each magnet <NUM> may have a second-longest dimension (a width, in one case) that extends or is oriented or aligned radially (e.g. extends along a radial line) as in the embodiment of <FIG>; or that extends or is oriented or aligned generally circumferentially as in <FIG>. Each magnet <NUM> may have a third-longest dimension (thickness) that extends or is oriented or aligned radially (e.g. extends along a radial line) as in <FIG>. In this configuration the magnets <NUM> can also be considered to be circumferentially aligned.

In the embodiment of <FIG> the face of the magnets <NUM> with the north poles <NUM> can be arranged to face radially inward, toward the central axis A of the assembly <NUM>, which controls how the magnetic circuit is completed by forcing the magnetic field through the attraction member <NUM>. This arrangement of inwardly-facing north poles <NUM> may be utilized when the magnets <NUM> are at an angle, relative to a radial line (on the radially outer side of the magnet <NUM> in one case), of equal to or greater than <NUM> degrees as shown in <FIG>, and also <FIG>.

In arrangements when the magnets <NUM> are arranged at angles equal to or less than <NUM> degrees (e.g. <FIG>) the polarity of the magnets <NUM>, or the inwardly-facing surfaces of the magnets <NUM>, can alternate between the north poles <NUM> and south poles <NUM>. In these cases the poles <NUM>, <NUM> of the magnets <NUM> can alternate such that a north pole <NUM> of each magnet <NUM> faces the north pole <NUM> of an adjacent magnet <NUM>. In addition, in these configurations an (exactly) even number of magnets <NUM> may be utilized to ensure the alternating pattern is maintained about the entire circumference of the magnet unit <NUM>. This alternating arrangement of magnets <NUM> (e.g. when arranged at angles of equal to or less than <NUM> degrees) maximizes the magnetic flux field to generate the highest level of available magnetic attractive force by physically isolating the opposite poles <NUM>, <NUM> of adjacent magnets <NUM> to avoid a magnetic short-circuit between adjacent magnets <NUM>.

The arrangement shown in <FIG> (e.g. magnets <NUM> arranged at angles of equal to or less than <NUM> degrees) can also reduce the adverse effects from the repulsive forces between adjacent magnets <NUM>. Such a repulsive force will occur when the magnetic field is flowing from north <NUM> to south poles <NUM> on a magnet <NUM>, and the magnetic field from an adjacent magnet <NUM> is flowing in the same direction. These magnetic interactions can thereby be accommodated by the alternating pole arrangement to avoid a reduction in the net magnetic attractive force, which as noted above defines or primarily determines the separation force between the magnet unit <NUM> and the attraction member <NUM>.

If the magnets <NUM> are arranged at angles of equal to greater than about <NUM> degrees (for example <FIG> (<NUM> degrees) and <FIG> (<NUM> degrees)), the number of magnets <NUM> can be even or odd, and the magnetic poles <NUM>, <NUM> may not need to be alternated due to dissipated magnetic forces. In the embodiment of <FIG> the strength of the magnets <NUM> may need to be relatively low since the adjacent magnets <NUM> may be more prone to a "short circuit" since the north poles <NUM> are not as physically isolated from the south poles <NUM> of an adjacent magnet <NUM>. In addition, the adjacent magnets <NUM> may experience greater repulsive forces since the poles <NUM>/<NUM> on one magnet <NUM> are not as physically isolated from the poles <NUM>/<NUM> on an adjacent magnet <NUM>. Thus in one case the magnets <NUM> are positioned at an angle other than perpendicular relative to a radial line in axial end view. However, in some cases the embodiment of <FIG>, or other similar arrangements which do not provide optimized magnetic performance, may be desired when the magnetic force is desired to be somewhat lessened to adjust and fine tune the separation force as desired. In addition, it should be noted that other magnet arrangements are possible, some of which are described in greater detail below.

In some cases magnet <NUM> which can be arcuate, and curve around the center A, in some cases matching the curvature of the curved channel <NUM>, <NUM>. However in this case, because an arcuate magnet <NUM> is used, the inner surface defined by the inner diameter of the arced magnet <NUM> will have a smaller surface area than the outer surface defined by the outer diameter of the arced magnet. The thicker the magnet <NUM>, the larger the difference in surface area.

As is well known, magnetic flux is the strength of the magnetic force times the area around the pole. When arcuate magnets <NUM> are used, the magnetic flux on the inner surface of the arcuate magnets <NUM> is greater than the magnetic flux on the outer surface, since the surface area of the inner surface is smaller than the surface area of the outer surface. It is known that the number of magnetic force lines (magnetic field) from north to south must be the same for each magnet <NUM>. With the surface area of the inner surface being smaller than that of the outer surface for arcuate magnets <NUM>, it follows that the flux density on the inner surface will be higher than that of the outer surface. The higher flux density results in a concentrated load on the inner surface of the arcuate magnets <NUM> that is higher than the load on the outer surface. Thus the use of arcuate magnets <NUM> provides a net total resultant magnetic force that is lower than what is achievable under an optimized design since the flux field entering the attraction member <NUM> has a smaller surface area than what is needed to effectively disperse and distribute the magnetic flux field. This results in saturation of the portion of the attraction member <NUM>, which causes underutilization of the total available magnetic field. It has been found that the largest impact on magnet performance is the surface area of the face of the magnet <NUM> that is normal to the pole of the magnet <NUM>.

In order to provide a balanced magnetic flux field, it may be desired for the inner annulus <NUM> of the magnet unit <NUM> to have an equal cross-sectional area, and/or equal volume, as the outer annulus <NUM>. However, the inner annulus <NUM> can have a smaller diameter than that of the outer annulus <NUM>. Thus as shown for example in <FIG>, <FIG> and <FIG>, the inner annulus <NUM> of the magnet unit <NUM> can be thicker, in the radial direction, than the outer annulus <NUM>, to provide an equal cross-sectional area and/or volume such that magnetic flux in the inner <NUM> and outer <NUM> annuli are equal.

In some existing designs, the flux field around the ends of one magnet <NUM> may be in the same direction as those of an adjacent magnet <NUM>. These aligned flux forces produces a repelling force and can cause the magnets <NUM> to eject from the magnet unit <NUM>, which can in turn cause the magnets <NUM> to be damaged or lost. The ejection force can also make assembly and repair of the magnet unit <NUM> difficult, and can require special processes and tools. Additionally, in some existing designs, as the magnets <NUM> are installed, each magnets <NUM> is biased to shift away from the adjacent magnet <NUM> due to the repelling magnetic fields. Thus, in this case the last few magnets <NUM> to be installed may require use of a special tool to reach into the magnet coupler <NUM>, and push the aside the existing magnets <NUM> while installing the last few magnets <NUM>.

The axial length of the channel <NUM>, <NUM> (and/or the axial length of each magnet <NUM>) can vary depending on the magnetic flux field desired to be generated at the end of the magnet coupler <NUM>. The channel <NUM>, <NUM> may have an axial length that is about equal to the axial length of the magnets <NUM> or slightly greater (within about <NUM>% in one case, or about <NUM>% in another case, or within about <NUM>% in another case) such that the channel <NUM>, <NUM> closely axially receives the magnets <NUM> therein. In addition, the axial position of the channel <NUM>, <NUM> can be adjusted as desired. For example in the embodiment of <FIG> and <FIG> the upstream portion 102a of the magnet coupler <NUM>, and its channel portion <NUM>, can have the same axial length as the downstream portion 102b and its channel portion <NUM>. In this case the channels <NUM>, <NUM> and magnets <NUM> are axially centered in the magnet coupler <NUM>. In this scenario the magnetic force on each axial side of the magnet coupler <NUM> will be the same (assuming other conditions that can effect magnetic force are identical; for example, assuming the upstream 102a and downstream 102b portions are made of the same material, that their webs <NUM> have the same thickness, etc.).

However if desired the magnet coupler <NUM>/channels <NUM>, <NUM> can be asymmetrical as shown in <FIG> (wherein <FIG> is disclosed herein, but not part of the claimed invention, due to the particular orientation of the magnets shown therein) such that one of the upstream 102a or downstream 102b portions and/or their channels <NUM>, <NUM> are longer than the other. In this case more of the length of the magnets <NUM> are received in one of the upstream 102a or downstream 102b portions. For example, in one case one of the upstream 102a or downstream 102b portions can have up to <NUM>/8th of the axial length of the combined length of the channels <NUM>, <NUM> and/or up to <NUM>/8th of the axial length of the magnets <NUM> therein, and the other one of the upstream 102a or downstream 102b portions can have the remaining (as little as <NUM>/8th, in the described embodiment) of the length of the combined channels <NUM>, <NUM> or magnets <NUM> therein. The upstream 102a or downstream 102b portion having the smaller portion of the magnets <NUM>/channels <NUM>, <NUM> will have the weaker magnetic flux field compared to the other having the larger portion of the magnets <NUM>/channels <NUM>, <NUM>.

The magnetic force on each axial side of the magnet coupler <NUM> can also be varied depending upon the method/mechanism used to join the upstream 102a and downstream 102b portions of the magnet unit <NUM>. In one case the upstream 102a and downstream 102b portions are welded at the joint <NUM> to form a welded joint therebetween, although care should be taken that the heat from the welding process does not damage the magnets <NUM>. In another case the upstream 102a and downstream 102b portions each have threaded surfaces <NUM> as noted above and are thus joined at the joint <NUM> by a threaded connection, but could also be joined by a variety of other mechanisms/methods, such as press fit, rabbiting, retaining rings or the like.

The joint <NUM> in the magnet coupler <NUM> can cause a flux field leakage, which can vary depending upon the nature of the joint <NUM>. For example, the magnetic flux field of the magnet coupler <NUM> can behave similar to fluids that want to travel the path of least resistance. The point of flux field leakage at the joint <NUM> of the magnet coupler <NUM> creates an area of resistance, which aids in the division of the magnet field in the magnet coupler <NUM>. Thus, differing types of joints <NUM> will permit or block magnetic fields to pass therethrough by differing amounts.

For example, certain joints <NUM> may present a high flux field impedance and block magnetic fields, and thus tend to magnetically isolate the upstream 102a and downstream 102b portions, which can provide greater control over certain performance parameters. Other joints may have a relatively low flux field impedance to allow/transmit magnetic fields and thus tend to magnetically couple the upstream 102a and downstream 102b portions, which can provide greater magnetic coupling strength and separation force. If desired a gasket or other component can be positioned in, at or adjacent to the joint <NUM> to provide a more predictable control of the flux field impedance at the joint <NUM>. The use of a gasket or component may be more practical when the upstream 102a and/or downstream 102b portions are made from a paramagnetic or diamagnetic material. The configuration and assembly of the magnet coupler <NUM> can thus be varied to adjust the force generated at each end thereof to adjust the breakaway features and other magnetic performance of the breakaway assembly <NUM>.

In addition, the materials of the upstream 102a and/or downstream 102b portions of the magnet coupler <NUM> can be varied to adjust the magnetic field. For example, the upstream 102a and downstream 102b portions can be made of various and different ferromagnetic metals or alloys that have differing saturation points. The upstream 102a or downstream 102b portion that is made of material having a lower saturation point will generate a lower magnetic force. If only one side of the magnet coupler <NUM> is desired to generate a magnetic force, then one of the portions 102a, 102b can be made from a ferromagnetic material and the other portion can be made of a paramagnetic or diamagnetic material, such as <NUM> series stainless steel or <NUM> grade of aluminum, and focus the magnetic flux at one end of the magnet coupler <NUM>.

Magnets <NUM> can often be brittle and therefore it may be desired to position such magnets <NUM> to avoid receiving direct impacts, or dissipating loads. The magnet unit <NUM> disclosed herein protects the magnets <NUM> when they are housed in the closed channels <NUM>, <NUM> of the magnet coupler <NUM>, and the magnets <NUM> are protected from direct impact. The closed channels <NUM>, <NUM> allows the end surfaces of the magnets <NUM> to be recessed such that the attraction member <NUM> does not physically engage or contact the magnets <NUM>, but instead engages or contacts the magnet coupler <NUM>. In addition, the efficient design and layout of the magnet unit <NUM> maximizes the use of the magnetic flux field and enables the magnet unit <NUM> to have a relatively small diameter, enabling the breakaway assembly <NUM> to have a smaller profile.

Another concern with magnets <NUM> is that they can be subject to corrosion. In order to address this issue magnets <NUM> are often coated or plated with various ferromagnetic metals, plastics or other materials. However, if these coatings are damaged the magnets <NUM> will be prone to corrosion. Thus care must be taken during assembly and storage of the breakaway assembly <NUM> to ensure the coating or plating of the magnets <NUM> is not damaged. The magnet coupler <NUM> helps to protect the magnets <NUM> from corrosion by protecting them during the installation process and during use. The design provides a magnet unit <NUM> with fully encapsulated magnets <NUM> that are sealed in an airtight and/or water-tight manner as a single subassembly that provides ease of handling and assembly, and provides protection to the encapsulated magnets <NUM>.

Another issue that can arise is that magnets <NUM> may attract metal particles and other items that are attracted to a magnetic field. When such items or particles are positioned on the magnet <NUM> and/or attraction member <NUM>, such items or particles can be trapped and impacted when the attraction member <NUM> and magnet unit <NUM> engage each other, thereby providing a pressure point that can damage or crack the attraction member <NUM> or magnet unit <NUM>. However, in the current design the magnets <NUM> are positioned in the closed channels <NUM>, <NUM>. Thus the magnets <NUM> are protected, and the end face of the magnet unit <NUM>, which can be made of a more rugged material, can bear the brunt of such impacts. In some cases, the radially outer surface of the magnet coupler <NUM> can be clad in aluminum or some other paramagnetic material to avoid collecting metal from the ambient environment onto the magnet coupler <NUM>.

Some existing designs allow for direct exposure of the magnets to the atmospheric elements, which can lead to damage and/or corrosion. In addition some existing designs have inefficiencies in their magnetic design in that certain portions of the magnetic field must pass through significant areas of air and do not contribute to the magnetic force. In addition some designs distribute the magnetic flux field through an unduly large surface area due to the pattern of the magnets, decreasing the effective strength of the magnetic field. In contrast, in the design disclosed herein the magnets <NUM> can be fully encapsulated in the magnet coupler <NUM>, and thus the magnet coupler <NUM> protects the magnets <NUM> from any corrosive material or debris. In addition, more magnetically efficient design is utilized.

<FIG>, <FIG> and <FIG> illustrate one particular embodiment wherein the magnet coupler <NUM> has a plurality of radially-aligned channels <NUM>, each of which closely receives a magnet <NUM> therein. In this case the magnets <NUM> are generally aligned along a radial line of the breakaway assembly <NUM>. The magnets <NUM> can be arranged such that the poles <NUM>, <NUM> are in alternating directions as in the layout of <FIG>. In addition in the case shown in <FIG> there can be twelve channels <NUM>/magnets <NUM> that are spaced apart on center by <NUM> degrees. Each magnet <NUM> (and corresponding channels <NUM>, <NUM>) can have a thickness (extending, in the embodiment of <FIG>, generally in the circumferential direction) of between about <NUM> (<NUM> inches) and about <NUM> (<NUM> inches), and more particularly between about <NUM> (<NUM> inches) and about <NUM> (<NUM> inches) in another case; a height (extending in the axial direction) of between about <NUM> (<NUM> inches) and about <NUM> (<NUM> inch), and more particularly between about <NUM> (<NUM> inches) and about <NUM> (<NUM> inches) in another case; and a length (extending in the radial direction) of between about <NUM> (<NUM> inches) and about <NUM> (<NUM> inches), and more particularly between about <NUM> (<NUM> inches) and about <NUM> (<NUM> inches) in another case. The length and height dimensions described above may be reversed if desires. These dimensions of the magnets <NUM> and channels <NUM>, <NUM> can also apply to the other embodiments described herein, regardless of orientation.

In the embodiment of <FIG>, <FIG> and <FIG>, the magnet unit <NUM> may include a magnet retainer <NUM>, as best shown in <FIG>, can be used to secure the magnets <NUM> in the desired position and orientation. In particular the magnet retainer <NUM> can include a base ring <NUM> (which can be analogous to and/or define the web <NUM>) and a plurality of generally wedge-shaped spacers <NUM> coupled to and extending axially away from the ring <NUM>. The spacers <NUM> define the generally rectangular prism-shaped channels <NUM> in which the magnets <NUM> are received. The magnet unit <NUM> may include a retaining ring <NUM> (<FIG>) received in a corresponding recess downstream of the magnet retainer <NUM> to keep the magnet retainer <NUM> and magnets <NUM> in place.

In this embodiment the magnet retainer <NUM> can be made of the same materials, such as ferromagnetic materials, as the attraction member <NUM> outlined above, and in one case is made of a magnetizable material. In this case the base ring <NUM> of the magnet retainer <NUM> can act as a shunting member, analogous to the web or end wall <NUM> of the embodiment of <FIG>, and the spacers <NUM> can become magnetized by the adjacent magnets <NUM>. Although the magnet retainer <NUM> is shown in conjunction with the embodiment of <FIG> and <FIG>, it should be understood that the magnet retainer <NUM> can be used in other configurations, in place of the magnet coupler <NUM> if desired.

As outlined above the coupling mechanism <NUM>, including the magnet unit <NUM> and the attraction member <NUM>, provide the sole or primary separation force to the breakaway assembly <NUM>. Starting in the coupled position, as shown in <FIG>, the connectors <NUM>, <NUM> are held together by the attractive force between the magnet unit <NUM> and the attraction member <NUM>. This attractive force can be at a minimum of <NUM> (<NUM> lbs. ) as per the currently applicable U. standards/regulations, but can be set at various other levels as desired. Thus use of magnets, along with the various adjustment factors described above, helps to ensure that the separation force of the breakaway assembly <NUM> is reliable and predictable, with relatively small variances between differing assemblies <NUM>. In one case the force required to separate the first <NUM> and second <NUM> connectors is in one case at least about <NUM> (<NUM> lbs. ), or in another case at least about <NUM> (<NUM> lbs. ) or in another case at least about <NUM> (<NUM> lbs. ), or in another case at least about <NUM> (<NUM> lbs. ), or in another case between about <NUM> (<NUM> lbs. ) and about <NUM> (<NUM> lbs. ), or at least about <NUM> (<NUM> lbs. ) in yet another case, or less than about <NUM> (<NUM> lbs. ) in one case, or less than about <NUM> (<NUM> lbs. ) in yet another case.

When it is desired to reconnect the breakaway assembly <NUM>, the connectors <NUM>, <NUM> can be pressed together in the axial direction, with the stems <NUM>, <NUM> engaging each other and then opening the associated poppet valves <NUM>, <NUM>. When sufficient force is applied the magnet unit <NUM> is positioned sufficiently close to the attraction member <NUM> that the attractive force between those components overcomes the repulsive force applied by the springs <NUM>, <NUM>, and the breakaway assembly <NUM> is retained in the open position shown in <FIG>.

The fluid in the fluid path <NUM> can sometimes experience pressure spikes, pressure shocks or line shocks due to uneven operation of the pump <NUM>, pressure imposed by operation of the user, or by other forces which may be relatively short in duration and tend to cause undesired separation (collectively termed a force spike herein). For example, in conventional fuel systems force spikes can be caused by a shut-off valve in the nozzle <NUM> closing the fluid path <NUM>, while the pump <NUM> continues to operate for short period of time. Force spikes can also be caused by the user jerking on the hose <NUM>, or from other sources. In many pressure spikes situations, the pressure spike has relatively low energy and may dissipate as it travels through the fluid path, since the fluid may be considered to be incompressible and have a relatively high energy transfer rate. However in this case the pressure spike may be present over a relatively long time period.

In some existing systems the force spike can apply a force to the poppet valve <NUM> of the downstream connector <NUM> or other components of the downstream connector <NUM>. In existing single use breakaways, the connecting member that connects the upstream <NUM> and downstream <NUM> connectors can be relatively rigid and can shear or break when a sufficient force spike force is applied, causing an undesired separation. Some reconnectable breakaways are better at handling impulse loads generated from, for example, a user jerking on the hose <NUM>, but a sufficiently high force by user force can still cause separation. Reconnectable breakaways that use compression or canted coil springs may lack sufficient response time; e.g. may not be able to transmit the load through the coils in sufficient time, which can lead to damage to the compression or canted coil spring.

The breakaway assembly <NUM> illustrated in for example <FIG> and <FIG> is configured to accommodate force spikes without causing damage to the components and without undue undesired separation. In particular, upstream connector <NUM> can include an inner member <NUM> (e.g. defined in one case by portions of the upstream connector <NUM> other than the magnet unit <NUM>) that has a limited range of axial movement or "float" relative to the magnet unit <NUM> to allow the assembly <NUM> to accommodate some force spikes without causing undesired separation events. The inner member <NUM> can be an annular component that extends entirely circumferentially around the fluid path <NUM>. The magnet unit <NUM> can thus be considered to be movably mounted within the upstream connector <NUM>, which enables the assembly <NUM> to accommodate force spikes in the system without causing separation.

In particular, the magnet unit <NUM>/magnet coupler <NUM> can have a generally annular skirt <NUM>, which can be part of or integral with the body of the magnet coupler <NUM>. The skirt <NUM> is positioned upstream of the magnets <NUM>, defining a shoulder <NUM> and an annular recess <NUM> positioned upstream of the shoulder <NUM>. An annular retaining ring <NUM> is positioned in the recess <NUM>. The magnet unit <NUM> further includes a retaining washer <NUM> positioned adjacent to, and axially downstream from, the retaining ring <NUM>.

The inner member <NUM> has a lip <NUM> positioned adjacent to, and axially spaced apart from, the retaining washer <NUM> when the assembly <NUM> is in the position shown in <FIG>. A first gap <NUM> is positioned between the lip <NUM> and the retaining washer <NUM> during normal operating conditions. A biasing element or resilient component <NUM> is positioned in a recess of the inner member <NUM> and can be in compression and engaging both the inner member <NUM> and the retaining washer <NUM>, and can include or take the form of a wire wave spring or other spring or resilient member having a predetermined preload. The resilient component <NUM> biases the inner member <NUM> to its rest or axial inner position, shown in <FIG>, and can be fluidly isolated from the fluid path <NUM>.

When a pressure spike propagates through the fluid path <NUM> and/or an impulse load is applied (e.g. by a user) the applied force can cause the inner member <NUM> and the poppet valve <NUM> of the upstream connector <NUM> (carried therewith) to move axially away from the magnet unit <NUM> and upstream connector <NUM>. As shown in <FIG> in one case the relative movement can appear as the inner member <NUM> and poppet valve <NUM> moving upstream, as compared to <FIG>, to an actuated or axial outer position. The inner member <NUM> can move upstream in a relative direction until the lip <NUM> of the inner member <NUM> engages the retaining washer <NUM>, thereby eliminating the first gap <NUM> of <FIG>, while introducing a second gap <NUM> as shown in <FIG> between the shoulder <NUM> and the downstream face of the inner member <NUM>. The magnet unit <NUM> and the attraction member <NUM> remain magnetically coupled during such force-spike induced movement, and the full stroke of the force-spike accommodating movement is defined by the first gap <NUM> of <FIG>, which gap <NUM> is eliminated in <FIG> during full movement of the inner member <NUM>. Of course, the inner member <NUM> does not necessarily need to move a full stroke to accommodate force spikes, and the gap <NUM> will in such cases be reduced/narrowed but not necessarily eliminated. In the manner the upstream connector <NUM> can have a gap introduced therein to accommodate force spikes, while the upstream <NUM> and downstream <NUM> connectors remain coupled.

If the force spike overcomes the resistance of the resilient component <NUM>, then the inner member <NUM>/assembly <NUM> will shift axially out, up to a fixed distance, to its force-spike accommodating position shown in <FIG>. The associated poppet valve <NUM> remains open and does not shift to its closed position, even when the inner member <NUM> is in its force-spike accommodating position. The inner member <NUM> can move to its force-accommodating position, while the remaining portion of the connector <NUM> and/or the other connector <NUM> remain relatively fixed. Since the spike forces are typically a quick pulse, once the inner member <NUM> shifts to the pressure-spike or force-spike accommodating position and the force spike has sufficiently diminished, the resilient component <NUM> will quickly urge the assembly <NUM> back to its position shown in <FIG>, wherein the downstream face of the inner member <NUM> engages and is pressed against the shoulder <NUM> of the magnet unit <NUM>. It should be noted that, when in the force-spike accommodating position shown in <FIG>, a sufficient separation force, applied either externally or by a sufficiently high pressure spike or combinations thereof, will still cause the magnet unit <NUM>/upstream connector <NUM> to separate from the attraction member <NUM>/downstream connector <NUM> in a separation event as described above.

The assembly <NUM> can accommodate force spikes that propagate in both the upstream direction and the downstream direction. In particular, both such force spikes can cause the same relative movement of the assembly from its rest position of <FIG>, as shown in <FIG>. Thus the resilient component <NUM> can accommodate and absorb the pressure or spike force in either direction. In addition, when a user jerks on the hose <NUM>, applying a direct physical force that tends to want to separate the assembly <NUM>, the resilient component <NUM> can help to absorb such forces and reduce breakaway events.

The resilient component <NUM> will have a predetermined preload force and compression point load. The resilient component <NUM> and maximum size of the gap <NUM> will both limit the stroke of the inner member <NUM> to a predetermined distance to ensure that the seal <NUM> on the upstream outer circumferential end of the downstream connector <NUM> is not pulled out of the bore, or out of contact with, of the inner surface of the upstream connector <NUM> when the assembly <NUM> is in its force-spike accommodating position. Thus the maximum stroke distance (e.g. axial dimension of the gap <NUM> and/or gap <NUM>, possibly shortened by the compressed length of the resilient component <NUM>) may be relatively short, such as less than about <NUM> (<NUM>/<NUM> inch) in one case, or less than about <NUM> (<NUM>/<NUM> inch) in another case, or less than about <NUM> (<NUM>/<NUM> inch) in another case, or less than or equal to about <NUM> (<NUM>/<NUM> inch) in another case, and greater than about <NUM> (<NUM>/<NUM> inch) in yet another case.

The force required to cause the assembly <NUM> to move to its force-spike accommodating position may be set to a lower value than the separation force. For example, if the separation force is set to <NUM> (<NUM> lbs. ), then the force required to cause the assembly <NUM> to move to its force-spike accommodating position can be set at a value less than <NUM> (<NUM> lbs. ), for example about <NUM> (<NUM> lbs. ) in one case. The assembly <NUM> may be able to accommodate various levels of force spikes, that are less than the separation force, such at least about <NUM> (<NUM> lbs. ) in one case, or at least about <NUM> (<NUM> lbs. ) in another case, or at least about <NUM> (<NUM> lbs. ) in yet another case, or greater than about <NUM>% of the separation force in one case, or greater than about <NUM>% of the separation force in another case, or less than the separation force in one case, or less than about <NUM>% of the separation force in yet another case. The force required to induce force-spike accommodation should be high enough to accommodate meaningful force spikes, but not so high as to risk being ineffective and effectively overridden by a breakaway event, and not so low as to enable frequent force-spike accommodation which can cause fatigue of the various components that accommodate force spikes.

In such a force spike event, the energy of the force spike is absorbed by the resilient component <NUM>. This accommodation of force spikes reduces unintended separations and improves the fuel dispensing experience. In addition, allowing the inner member <NUM> to move/float relative to the remainder of the upstream connector <NUM> isolates the joint <NUM> of the magnet coupler <NUM> from fluid spike forces. Instead of applying forces to the joint <NUM>, the spike forces are applied to annular areas, such as the retainer washer <NUM>, retaining ring <NUM>, and recess <NUM> of the assembly <NUM>, which can be designed and configured to accommodate applied loads.

In addition or in the alternative, instead of having the magnet unit <NUM> move or "float" to accommodate force spikes, the attraction member <NUM> can instead be configured to "float" in the downstream connector <NUM> such that the downstream connector <NUM> can accommodate force spikes in either direction. In this embodiment, the resilient component <NUM> (and retaining ring <NUM> and retaining washer <NUM>, if desired) are positioned adjacent to the attraction member <NUM> (e.g. in gap <NUM> in one case) in manners which are apparent to a person of ordinary skill in the art as taught by the illustrated embodiments in <FIG> and <FIG>. In this case, when there is a force spike in the fluid path <NUM>, the attraction member <NUM> may move slightly relatively axially, such as downstream, and the associated resilient component <NUM> is compressed, absorbing the force of the force spike. Once the force spike is dissipated, the attraction member <NUM> returns to its original position as biased by the spring/resilient member <NUM>.

As outlined above the magnet unit <NUM> and/or attraction member <NUM> can use springs or other energy-absorbing devices to accommodate force spikes in the system. In the case where both the magnet unit <NUM> and attraction member <NUM> are configured to accommodate force spikes, the force-spike accommodation system can be arranged to accommodate force spikes in a staged manner. For example, the resilient components <NUM> can have different spring constants or otherwise be arranged to be activated at different levels of force. In this case one of the force-spike accommodation systems can be activated at a lower pressure or force, and the other one of the force-spike accommodation systems can be activated at a higher pressure or force. In one case the higher force-spike accommodation system can be configured to be activated just as the lower force-spike accommodation system reaches its limit; that is in one case as or just before the gap <NUM> is eliminated. Such a "double floating" system can thereby bracket spike forces and accommodate them in a more efficient manner, and provide the ability the accommodate more powerful force spikes.

It should be further understood that the force spike accommodation system, while shown herein in conjunction with a magnetic coupling system <NUM>, is not necessarily limited to use with such a magnetic coupling system <NUM>. Instead the force spike accommodation system and features can be used with nearly any system or component for coupling the first <NUM> and second <NUM> connectors, including mechanical coupling systems.

In a further alternative embodiment for accommodating force spikes, rather than using the resilient component <NUM>, as shown, in one case, in <FIG> a magnetizable material <NUM> can be coupled (e.g. by a schematically-shown threaded joint <NUM> in one case, but various other coupling mechanisms can be used) to the inner member <NUM> of the upstream connector <NUM>, and the magnets <NUM> can act as a biasing element to aid in accommodating force spikes. The magnetizable material <NUM> is positioned adjacent to, but not directly coupled to, the shoulder <NUM> of the magnet unit <NUM>/magnetic coupler <NUM>. The magnetizable material <NUM> can be for example a ferromagnetic alloy member having a saturation point greater than <NUM> Tesla. The magnetizable material <NUM> can be magnetically attracted to the magnets <NUM>/magnet unit <NUM> (with a force lower than the separation force) to allow floating of the magnet unit <NUM> to accommodate line shock or pressure shock as described above. When a line shock, impulse load or force spike of sufficient force is experienced in the embodiment of <FIG>, the inner member <NUM> will move relatively upstream (and/or the connector <NUM> will move relatively downstream), narrowing or closing the gap <NUM>, while another gap <NUM> (<FIG>) opens between the magnetizable material <NUM> and the shoulder <NUM>.

When a magnetic force is used to control and accommodate force spikes as per the embodiment of <FIG> for example, one end (e.g. the upstream end) of the magnet unit <NUM> may be desired to have a lower magnetic force than the other end (e.g. the downstream end) to ensure the force required to cause the assembly <NUM> to move the assembly <NUM> to its force-spike accommodating position (<FIG>) is lower than the separation force. This can be accomplished in some of the manners outlined above, such as the having the downstream portion 102b of the magnetic coupler <NUM> being made of a material having a higher saturation point then the upstream portion 102a, thus increasing its efficiency and separation force, or by use of a gasket at the joint <NUM>, by varying position of the magnets <NUM> in the magnet coupler <NUM>, by increasing the thickness of the web, etc. In one case the one of the portions 102a/102b (the downstream portion 102b in one case) of the magnetic coupler <NUM> can be made of a material having a saturation point of greater than <NUM> Tesla, and the other portion 102a/102b (the upstream portion 102a) can be made of a material having a saturation point of less than <NUM> Tesla, or be made of a paramagnetic or diamagnetic alloy or material. In the case where a spring or other resilient component <NUM> is used to accommodate force or pressure spikes, the upstream portion 102a of the magnetic coupler <NUM> can be made of a paramagnetic or diamagnetic material, since a magnetic field may not be needed on the upstream side of the magnet coupler <NUM>.

Another way to provide a reduced magnetic force on the upstream end of the magnet unit <NUM>/magnetic coupler <NUM> would be to simply increase the thickness of the web <NUM> (e.g. the axially extending thickness at the upstream end) of the upstream portion 102a, which shunts the magnetic flux to reduce the magnetic force to the desired level. However it has been found that if the web thickness <NUM> is made too great (greater than about <NUM> (<NUM>/<NUM> inch) in one case) the attraction force may be lowered too much, and thus may not be practical. On the other hand, if the web thickness <NUM> is too small (less than about <NUM> (<NUM>/<NUM> inch) in one case) the strength/integrity of the magnet unit <NUM> may be compromised. Another way to provide a reduced magnetic force on the upstream end of the magnet unit <NUM> would be to reduce the diameter of the magnet unit <NUM>, which reduces magnetic efficiency.

It should also be understood that the magnetic-based system for dissipating force spikes (<FIG> and <FIG>) can be used in combination with the spring-based system for dissipating force spikes (<FIG>, <FIG>, <FIG> and <FIG>) to provide two separate systems, usable together, for accommodating force spikes, acting either on the same components, or on different components to provide staged force spike accommodation as outlined above. It should also be noted that the magnetic pressure dissipation system can also be used in the downstream connector <NUM>, with corresponding structure to that described above being provided and adjusted as needed.

Thus, it can be seen that when the magnet unit <NUM> is used to accommodate force spikes, the magnet unit <NUM> serves a dual purpose in controlling the separation force and also controlling the force-spike accommodation force. Accordingly the magnet unit <NUM> provides a usable magnetic field on both axial ends thereof, where the relative strength of the magnetic field on each end can be controlled as desired. Alternatively the magnet unit <NUM> may provide a usable magnetic field on only one end thereof.

The breakaway assembly <NUM> described above is generally designed for use with convention fuels, such as gasoline, diesel, etc. that are not stored and/or delivered under significant pressures. However the magnetic breakaway design and/or similar or analogous structures can also be used in systems that store and deliver fuel or fluid under relatively high pressure, such as CNG, hydrogen, LPG or the like. In these cases the fuel can be stored and dispensed under pressure (in one case in the range of between about <NUM> MPa (<NUM> psi) and about <NUM> MPa (<NUM>,<NUM> psi), and in another case between about <NUM> MPa (<NUM>,<NUM> psi) and about <NUM> MPa (<NUM>,<NUM> psi), or at least about <NUM> MPa (<NUM> psi) in one case, of at least about <NUM> MPa (<NUM> psi) in one case, or at least about <NUM> MPa (<NUM>,<NUM> psi) in another case, or in another case at least about <NUM> MPa (<NUM>,<NUM> psi), or less than about <NUM> MPa (<NUM>,<NUM> psi) in one case, or less than about <NUM> MPa (<NUM>,<NUM> psi) in another case).

The breakaway assembly <NUM>' shown in <FIG> is somewhat analogous to those shown in <FIG>, with the same reference numbers (either with or without a "prime" indicator and/or a letter indicator in certain cases) used for the same or analogous components, although the flow direction in the drawings of <FIG> is opposite to that of the <FIG> embodiment. Thus for example the breakaway assembly <NUM>' of <FIG> includes the first or upstream connector <NUM>' and the second or downstream connector <NUM>', and fluid to be dispensed flows in a left-to-right direction. The first connector <NUM>' includes a connection structure <NUM> having a series of generally axially-extending, circumferentially spaced flanges or jaws <NUM> that can releasably engage a circumferentially extending recess/ramp <NUM> on the second connector <NUM>', as will be described in greater detail below. The second connector <NUM>' has a neck portion <NUM> which carries the recess <NUM> on a radially outer surface thereof, and a fixed shaft member <NUM> is positioned in the second connector <NUM>'. The shaft member <NUM> has an inner cavity <NUM> thereon and facing upstream. A poppet valve <NUM>' is positioned in the second connector <NUM>'. A valve <NUM>, such as a curtain valve having curtain valve member, shuttle valve, closure valve or slider <NUM> is movably positioned in the first connector <NUM>', and movable between an upstream/open position, shown in <FIG>, and a downstream/closed position, shown in <FIG> and <FIG>.

The first connector <NUM>' includes a center shaft or tubular structure <NUM> about which the slider <NUM> is movably/slidably mounted. The slider <NUM> includes an annular sealing structure <NUM> that closely fits about the center shaft <NUM>. The center shaft <NUM> can be hollow, having a central cavity <NUM> therein and a plurality of radially-extending openings <NUM> (or at least partially radially-extending openings <NUM> which can extend primarily radially, or form an average angle of greater than <NUM> degrees relative to a central axis in one case, or greater than <NUM> degrees in another case, or strictly radially extending in yet another case) which form part of the fluid path <NUM>, positioned adjacent to a downstream end thereof, that are in fluid communication with the cavity <NUM>. The first connector <NUM>' has a pair of seals <NUM>, <NUM> positioned on the center shaft <NUM>. The upstream seal <NUM> is positioned upstream of the openings <NUM>, and the downstream seal <NUM> is positioned downstream of the openings <NUM>.

When the assembly <NUM>' is in its connected configuration, as shown in <FIG>, the downstream end of the center shaft <NUM> is received in the inner cavity <NUM> of the shaft member <NUM>. In this position the downstream seal <NUM> of the first connector <NUM>' engages the radially inner surface of the shaft member <NUM> (e.g. the radially outer surface of the inner cavity <NUM>) and the upstream seal <NUM> of the first connector <NUM>' engages the radially inner surface of the distal end of the neck portion <NUM>, to seal the fluid in the fluid path <NUM> as fluid flows from the upstream connector <NUM>' to the downstream connector <NUM>' as shown by the arrows in <FIG>.

In this manner fluid can flow down the cavity <NUM> of the center shaft <NUM>, radially outwardly through the openings <NUM> and encounter the poppet valve <NUM>'. The poppet valve <NUM>' includes a movable member <NUM> having a sealing surface <NUM>, and is biased to an upstream/sealing position by spring <NUM>'. When the poppet valve <NUM>' is closed its sealing surface <NUM> sealingly engages valve seat <NUM> on the shaft portion <NUM>, as shown in <FIG> and <FIG>. In contrast, when fluid of sufficient pressure acts on the poppet valve <NUM>', the movable member <NUM> moves downstream, compressing the spring <NUM>', and allowing fluid to flow past the poppet valve <NUM>' as shown in <FIG>. Thus when the assembly <NUM>' is in the configuration shown in <FIG>, under sufficient pressure fluid can flow to the nozzle <NUM> in the direction of the arrows shown in <FIG>.

When an axial separation force is applied to the first <NUM>' and second <NUM>' connectors, the slider <NUM> moves to a downstream position (in a manner which will be described in greater detail below), as shown in <FIG>. In this position the sealing structure <NUM> of the slider <NUM> extends over, and sealingly engages/covers, the openings <NUM> of the center shaft <NUM>, and thus blocks fluid flow as or in the manner of a curtain valve. The sealing structure <NUM> of the slider <NUM> simultaneously sealingly engages both seals <NUM>, <NUM> of the upstream connector <NUM>' to provide a secure seal. When first <NUM>' and second <NUM>' connectors are properly and fully reconnected, the slider <NUM> is retracted or moved upstream (in a manner which will be described in greater detail below), and the openings <NUM> are uncovered such that fluid can flow through the assembly <NUM>'.

As noted above, the connection structure <NUM> can include a plurality of axially-extending flanges <NUM> on the first connector <NUM>', wherein each flange <NUM> is circumferentially spaced from any adjacent flanges <NUM>. Each flange <NUM> may be movable or pivotable in the radial direction (e.g. be moved radially outwardly from the position shown in <FIG> to the position shown in <FIG> and <FIG>). Each flange <NUM> may be biased to be in its radially outward positions shown in <FIG> and <FIG>, by a spring <NUM> or the like that extends circumferentially around the base ends of the flanges <NUM> and urges the flanges <NUM> radially outwardly by a lever force, pivoting about pivot location <NUM>. Each flange <NUM> may also be axially coupled to and axially movable with the slider <NUM>.

When the slider <NUM>/connection structure <NUM> is in its upstream position or first axial position, as shown in <FIG>, the downstream ends of the flanges <NUM> are positioned radially inside the attraction member 106b and prevented from moving radially outward. This means that the flanges <NUM> are positioned in the recess <NUM> and securely grip the downstream connector <NUM>', preventing separation. In contrast, when the slider <NUM>/connection structure moves to its downstream or second axial position, as shown in <FIG> the downstream end of the flanges <NUM> protrudes axially beyond the attraction member <NUM>, enabling the flanges <NUM> to move radially outwardly, out of the recess <NUM> and thereby release the downstream connector <NUM>'. In this manner, the slider <NUM> can be positively axially coupled to the downstream connector <NUM>' when the assembly <NUM>' is in the coupled configuration, and the slider or closure valve <NUM> is released and not axially coupled to the downstream connector <NUM>' when the assembly <NUM>' is in the disconnected configuration. In other words the downstream connector <NUM>' can be configured to move the slider or closure valve <NUM> to the closed position when the assembly <NUM>' moves from the connected configuration to the disconnected configuration.

Each flange <NUM> may include a surface <NUM> that is angled (i.e. extending at a non-parallel angle relative to the central axis) on its radially inner surface. The upstream connector <NUM>' may include a ramp or angled surface <NUM> that engages the ramp or angled surfaces <NUM> when the slider <NUM> is in its upstream position as shown in <FIG>. When the slider <NUM> slides to its downstream position, as shown in <FIG> and <FIG>, the angled surfaces <NUM>/<NUM> slide axially relative to each other, and the flanges <NUM> are thereby positively moved to their radially outer position, releasing the downstream connector <NUM>'. In contrast, when the slider <NUM> moves returns to its upstream position (e.g. moving from the position of <FIG>/<FIG> to the position of <FIG>), angled surfaces <NUM> on the radially outer surfaces of the flanges <NUM> engage an angled surface <NUM> on the attraction member 106b to positively move the flanges <NUM> to their radially inner position. However it should be understood that the connection structure <NUM> can take any of a wide variety of other forms or mechanisms for releasably coupling the slider <NUM> and the downstream connector <NUM>', such as various ramps, interengaging fingers, interengaging geometry, magnetic couplings, spring connections, etc..

A coupling mechanism <NUM>' can be used to secure the slider <NUM> in its upstream position and thereby axially secure the upstream <NUM>' and downstream <NUM>' connectors, and to solely or primarily supply the separation force to the breakaway assembly <NUM>'. The coupling mechanism <NUM>' can include a magnet unit <NUM>' that is coupled to or forms part of the slider <NUM> that is the same as or analogous to the magnet unit <NUM>' described above. However in this case the magnet unit <NUM>' is coupled to the slider <NUM> and movable with the slider <NUM> as will be described in greater detail below. In addition, the assembly <NUM>' can include a pair of attraction members 106a, 106b that are the same as or analogous to the attraction member <NUM> outlined above. In particular, the attraction member 106a of the embodiment of <FIG> is positioned at an upstream end of the upstream connector <NUM>', and magnetically engages the magnet unit <NUM>'/slider <NUM> when the magnet unit <NUM>'/slider <NUM> is in its upstream position to provide the separation force. In addition, the upstream attraction member 106a may axially float in the system such that the attraction member 106a is axially movable, but constrained in such movement in both axial directions by a fixed body <NUM> and retaining washer <NUM>, respectively. The attraction member 106a may be biased in the upstream direction by spring or resilient element <NUM>.

The attraction member 106b is positioned at a downstream end of the upstream connector <NUM>', and magnetically engages the magnet unit <NUM>'/slider <NUM> when the magnet unit <NUM>'/slider <NUM> is in its downstream position, to provide a desired reconnection force. The magnet unit <NUM>' can be magnetically attracted to the attraction members 106a, 106b, and by the same or variable amounts by for example adjusting the properties of the magnet unit <NUM>' and/or attractions members 106a, 106b as outlined above. In one embodiment, the attraction of the magnet unit <NUM>' to the downstream attraction member 106b (when the slider <NUM> is in its downstream position) is greater than the attraction of the magnet unit <NUM>' to the upstream attraction member 106a (when the slider <NUM> is in its upstream position). Thus in this case the reconnection force of the assembly <NUM>' may be greater than the separation force. This can provide a safety feature as described in greater detail below.

When the assembly <NUM>' is in the fully connected configuration shown in <FIG>, the slider <NUM> is in its upstream position, and held in position due to magnetic engagement between the magnet unit <NUM>' and the attraction member 106a. During a breakaway event, a downstream axial force is applied to the second connector <NUM>', which is transmitted to the slider <NUM> due to the engagement of the ramp <NUM> of neck portion <NUM> and the angled surfaces <NUM> of the flanges <NUM>. Accordingly, an applied separation force is applied to, and must first overcome, the magnetic attraction between the magnet unit <NUM>' and the upstream attraction member 106a, which causes the slider <NUM> to move to its downstream position shown in <FIG>. As the slider <NUM> moves to its downstream position the distal end of the flanges <NUM> move axially clear of the attraction member 106b, which enables the flanges <NUM> to move to their radially outward position as biased by the spring <NUM>. This, in turn, causes the flanges <NUM> to release the downstream connector <NUM>', and the slider <NUM> fully moves to its downstream position.

When the downstream connector <NUM>' is separated from the upstream connector <NUM>', the downstream connector <NUM>' imparts a downstream force to the slider <NUM>, thereby securely pulling the slider <NUM> into its closed position to seal the openings <NUM> by the seals <NUM>, <NUM> as described above. In addition since the slider <NUM> is moving downstream, the force of the pressurized fluid upstream of the slider <NUM> urges the slider <NUM> to its closed position thereby providing a reliable seal. As the downstream connector <NUM>' separates from the upstream connector <NUM>' the poppet valve <NUM>' in the downstream connector <NUM>' is closed as biased by its spring <NUM>, which can overcome the reduced pressure in the fluid path <NUM> due to closure of the openings <NUM>. Thus, after a separation event both connectors <NUM>', <NUM>' can be fluidly sealed in a reliable manner.

In order the couple the connectors <NUM>', <NUM>' and move the assembly <NUM>' to its connected configuration, the connectors <NUM>', <NUM>' may begin in an axially-spaced apart position, as shown in <FIG> and <FIG>. The connectors <NUM>', <NUM>' are then axially moved together and the second connector <NUM>' engages the slider <NUM> (<FIG>) and moves the slider <NUM> upstream (uncovering the openings <NUM> and opening the valve <NUM>) until the magnet unit <NUM> engages the upstream attraction member 106a. Once the second connector <NUM>' is sufficiently axially inserted, the flanges <NUM> are moved radially inwardly by the angled surfaces <NUM>, placing the spring <NUM> in tension. The flanges <NUM> then engage the ramp <NUM> and are received in the recess <NUM> to secure the connectors <NUM>', <NUM>' together. Once the connectors <NUM>', <NUM>' are connected and the curtain valve <NUM> is open, pressurized fluid flows into the downstream connector <NUM>' and opens the poppet valve <NUM>' therein due to the pressure exerted by the fluid on the poppet valve <NUM>', as shown in <FIG>.

In order to move the assembly <NUM>' from its disconnected configuration of <FIG> to its connected configuration of <FIG>, in one case a reconnection tool <NUM> as shown in <FIG> and <FIG> may be utilized. The connection tool <NUM> includes a pair of manually operable handles <NUM> that are operable coupled, via various linkages and pivot connections, to a first coupler <NUM> and a second coupler <NUM>. The first coupler <NUM> is a generally annular component configured to closely fit in a recess <NUM> on an outer surface of the first connector <NUM>'. The second coupler <NUM> is a generally annular component configured to fit over a lip <NUM> of the second connector <NUM>'.

When the connection tool <NUM> is in the configuration shown in <FIG>, and the handles <NUM> are oriented in a radial direction the first coupler <NUM> and second coupler <NUM> are relatively axially spaced apart. The connection tool <NUM> is then operated such that the handles <NUM> are pivoted about their pivot points <NUM> until they handles <NUM> are oriented in an axial direction, and the first coupler <NUM> and second coupler <NUM> are moved axially closer together, as shown in <FIG>, thereby pulling the second connector <NUM>' into the first connector <NUM>' as outlined above. In some cases the tool <NUM> may be provided to only certified trained personnel to ensure the connection and reconnection process is completed properly and that the system is properly inspected before and after separation.

When the slider <NUM> is in its downstream position (<FIG> and <FIG>), the magnet unit <NUM>' magnetically interacts with, and is thus magnetically coupled to, the downstream attraction member 106b. The downstream attraction member 106b thus acts as a security measure to lock the slider <NUM>/curtain valve <NUM> in its closed position, and requires a predetermined force to move the slider <NUM> away from the downstream position. In particular, the magnet unit <NUM>' and attraction member 106b together ensure that a sufficiently high force is required to return the slider <NUM>/curtain valve <NUM> to its open position so that only authorized/sufficiently trained personnel can reconnect the assembly <NUM>'. This can help to ensure that the assembly <NUM>' is properly assembled and that the parts are in good working order. In one case, the force required to move the slider <NUM>/curtain valve <NUM> away from its downstream position is about <NUM> (<NUM> lbs. ), or greater than the separation force in one case, or greater than about <NUM>% the separation force in one case, or less than the separation force in one case, or less than about <NUM>% of the separation force in another case. However, the inclusion of the attraction member 106b is optional and the attraction member 106b can be omitted if desired.

In some cases, the downstream connector <NUM>' may include a vent <NUM> (<FIG>) in the form of a relatively small opening that provides fluid communication between the fluid path inside the downstream connector <NUM>' (downstream of the poppet valve <NUM>') and the ambient atmosphere. In this case after a separation event when the poppet valve <NUM>' of the downstream connector <NUM> is closed, the vent <NUM> allows for a controller release of fluid that may be trapped by the poppet valve <NUM>' to reduce pressure in the system.

The assembly <NUM>' of <FIG> provides a robust and reliable shut-off valve in which the sealing functionality is provided by the sealing structure <NUM> of the slider <NUM> extending over and sealing the openings <NUM> of the center shaft <NUM>. In this case the sealing surfaces are entirely positioned inside the assembly <NUM>' in both the connected and unconnected states of the assembly <NUM>' and protected from external forces, and from dirt/debris. The slider <NUM>/curtain valve <NUM> allows flow or shuts off flow from radially outside the fluid path <NUM>/cavity <NUM>, as the slider <NUM> seals on the outer surface/diameter of the center shaft <NUM>. The existence of pressure in the cavity <NUM> of the center shaft <NUM>, when the slider <NUM>/curtain valve <NUM> is closed, exerts a force radially outwardly. However the slider <NUM>/curtain valve <NUM> is moveable axially between its open and closed positions. Thus the existence of radially exerted pressure in the cavity <NUM>/center shaft <NUM> does not affect operation of the slider <NUM>/curtain valve <NUM>, and the curtain valve <NUM> is thereby pressure balanced when the slider <NUM> is in its downstream/closed position, and the pressure of the fluid does not tend to either open or close the curtain valve <NUM>. In this case an external force is required to open or close the slider <NUM>/curtain valve <NUM>. In addition, when the slider <NUM> is in its downstream position both seals <NUM>, <NUM> engage the slider <NUM> to thereby trap/close the openings <NUM> for a strong seal. The curtain valve <NUM> thus reduces susceptibility to force spikes, although the assembly <NUM>' can include force-spike accommodation features as will be described below.

As noted above, the seals <NUM>, <NUM> are captured and internally positioned so that they resist removal. In contrast, in certain other designs the seals can be blown out of position during a separation event, and the person who reconnects the assembly may not notice the missing seals. However, the present design minimizes the chance for displacement of the seals <NUM>, <NUM>. Moreover, the angled surfaces <NUM> on the flanges <NUM> that axially connects the two connectors <NUM>', <NUM>' faces radially inwardly and are protected from damages. The corresponding angled ramp <NUM> faces radially outwardly but is also protected from damage when the assembly <NUM>' is in its connected configuration, and in addition the ramp <NUM> is easily visible for inspection after a separation event to ensure the ramp <NUM> is not damaged.

In addition, the magnet unit <NUM>' is directly coupled to the slider <NUM>/curtain valve <NUM>, which provides a quicker response in terminating the flow of fluid. Many current systems rely on pressure, flow and a biasing spring to close a check valve or the like. In those cases, if there is any debris in the fluid path <NUM> the valve can be held open and/or slow to close. In contrast, the assembly <NUM>' has no or little surfaces (e.g. surfaces that are perpendicular to the direction of the flow) that debris can collect on to prevent the valve <NUM> from closing, since the slider <NUM> is slidably positioned on, and slides axially over, the center shaft <NUM>. In addition any debris positioned on the center shaft <NUM> can be displaced and cleaned away by axial sliding of the slider <NUM> to provide a self-cleaning design.

The assembly <NUM>' and in particular the slider <NUM>/curtain valve <NUM> design provides a component in which, when the assembly <NUM>' is in its connected configuration, a relatively low number of parts in the upstream connector <NUM>' are exposed to pressure; e.g. the slider <NUM>, both seals <NUM>, <NUM>, the upstream threaded adapter <NUM>, the center shaft <NUM> and internal components of the downstream connector <NUM>'. After a separation event, when the curtain valve <NUM> is closed, the only components of upstream connector <NUM>' exposed to pressure due to pressurized fluid therein are the slider <NUM>, the valve <NUM>, the center shaft <NUM> and the upstream threaded adapter <NUM>. Thus by providing a relatively low number of parts exposed to pressure, the chances of a loss of pressure are reduced, and cost and complexity of the assembly <NUM>' can also be reduced.

As noted above, the angled engaging surfaces <NUM>, <NUM> that transmit the separation force are similarly internally positioned and protected in both states of the assembly <NUM>'. Finally, the flow path through the assembly <NUM>' is relatively straight with relatively little turns and change-of-direction provided to the fluid, which reduces pressure forces, reduces wear and tear on the assembly <NUM>', and presents less opportunities for clogs or flow obstructions.

Pressurized fuels may be exposed to pressure spikes due to, for example, connection of the fluid path to a compressor which causes pressure fluctuation during operation of the compressor. Pressure spikes may also occur when an operator jerks on the hose <NUM>. Since the fluid is compressible, but under relatively high pressure, shock waves (which can come from an upstream source such as a compressor or pump) may propagate through the system relatively quickly, presenting a high pressure spike over a relatively short period of time.

During a pressure spike event of the assembly <NUM>' of <FIG>, since the assembly <NUM>' is pressure balanced as described above, a fluid-based pressure spike may not directly lead to or cause separation of the assembly <NUM>'. Instead, a fluid-based pressure spike from an upstream source may instead apply increased pressure to the seals <NUM>, <NUM>. The seals <NUM>, <NUM> may become temporarily comprised and release or "burp" pressure or fluid into the surrounding volumes, such as inner cavity <NUM> of the shaft member <NUM>. It is possible that sufficient burping of fluid or pressure could eventually build up to a degree that relatively strong separation forces are applied to the assembly <NUM>'. In addition, an external separation forces, such as a user pulling on the hose <NUM> can impart separation forces that may need to be accommodated. Thus the pressure-spike/separation force accommodation features outlined above, such as the floating magnet unit <NUM>' and/or floating attraction member 106a, 106b may be utilized in the assembly <NUM>' of <FIG>.

In particular, as shown in <FIG> and <FIG>, the center shaft <NUM> of the upstream connector <NUM>' may have a retaining ring <NUM> received in a recess <NUM> on an outer surface thereof, retaining the washer <NUM> in place. When in the coupled arrangement and not accommodating a pressure spike, as shown in <FIG>, an axially-extending gap <NUM> is positioned between the washer <NUM> and the attraction member 106a, and the attraction member 106a is biased to the upstream position by spring <NUM>.

When the assembly <NUM>' experiences a pressure spike, the slider <NUM>, magnet unit <NUM>' and attraction member 106a, which remains magnetically coupled to the magnet unit <NUM>', can move slightly downstream relative to the rest of the assembly <NUM>, overcoming the spring force of the resilient component <NUM> and eliminating the gap <NUM> as the magnet unit <NUM>' and attraction member <NUM> move downstream. Such relative movement creates a new gap <NUM> upstream of the attraction member 106a, as shown in <FIG>, and compresses the spring <NUM>. When in the pressure spike accommodating position of <FIG>, if a sufficient separation force is applied to the assembly <NUM>', the magnet unit <NUM>' and slider <NUM> will separate from the attraction member 106a and move downstream, and the assembly <NUM>' will move to the configurations shown in <FIG> and <FIG>. However assuming that no separation force is experienced, once the pressure spike force is dissipated, the assembly <NUM>' will return to its position shown in <FIG>, as biased by the spring or resilient component <NUM> which seeks to expand back to its original position.

The gaps <NUM> and/or <NUM> can be relatively small, such as between about <NUM> (<NUM> inch) and about <NUM> (<NUM> inch), and about <NUM> (<NUM> inch) in yet another case since the shocks from a compressor/pump or the like may be relatively short in time. The gaps <NUM>/<NUM> in this case can be relatively small compared to the gap <NUM> of the embodiment shown in <FIG>, <FIG> and <FIG> to ensure that there is not movement in the assembly <NUM>' sufficient to pull any seals out of position. However, the gaps <NUM>/<NUM> in the embodiment of <FIG> and <FIG> may also be large enough (up to about <NUM> (<NUM> inches) in some cases) to accommodate downstream movement of the attraction member 106a due to a user jerking on the hose <NUM> in the same manner that a pressure spike may be accommodated.

Thus, it can be seen that that system described and shown herein can provide a fluid dispensing system that can use magnetic features to provide a separation force; that can use magnetic features to accommodate pressure spikes; that can provide valves that are robust and provide strong sealing features; that can accommodate pressure spikes with features other than magnets, and that provide the various other features and advantages described herein.

Having described the invention in detail and by reference to certain embodiments, it will be apparent that modifications and variations thereof are possible without departing from the scope of the invention as defined by the claims.

In some embodiments the channel may be positioned in both the first portion and the second portion.

In some embodiments at least part of each magnet may be positioned in both the first portion and the second portion, and wherein each magnet may be positioned such that a greater portion of the magnet is positioned in one of the first or second portions than in the other one of the first or second portions.

In some embodiments the magnet unit may have two opposite axial ends, and wherein the magnet unit may have a stronger magnetic force at one axial end as compared to the other axial end.

In some embodiments the first portion may include an end wall positioned at an axial end thereof adjacent to the channel and wherein the second portion may include an end wall positioned at another axial end thereof adjacent to the channel, and wherein the end walls may have differing thicknesses in the axial direction.

In some embodiments the magnet unit may be annular and may extend entirely around the fluid path.

In some embodiments the first portion and the second portion may be two discrete components that are coupled together, and wherein the first portion and the second portion may each be made of a magnetizable material.

In some embodiments the magnetic attraction between the attraction member and the magnet unit may define or primarily contribute to the separation force that is required to move the assembly from the first configuration to the second configuration.

In some embodiments each magnet may be generally shaped as rectangular prism and is aligned with a radial line of the breakaway assembly in axial end view.

In some embodiments each magnet may be generally shaped as rectangular prism and may be circumferentially arranged in the breakaway assembly in axial end view.

In some embodiments each magnet may be generally shaped as a rectangular prism and may form an angle of greater than <NUM> degrees and less than <NUM> degrees with respect to a radial line of the breakaway assembly in axial end view.

In some embodiments the channel may be a polygon in axial end view.

In some embodiments the channel may be circular in axial end view.

In some embodiments each magnet may be entirely enclosed in the magnet unit on all sides thereof, and the channel may be sealed in a fluid-tight manner to isolate the magnets therein from the surrounding environment.

In some embodiments the magnet unit may be configured such that an axial end surface thereof is configured to contact the attraction member when the assembly is in the first configuration.

In some embodiments the attraction member may be fixedly and non-movably coupled to the one of the first or second connectors, and wherein the magnet unit may be fixedly and non-movably coupled to the other one of the first or second connectors.

In some embodiments the attraction member may be fixedly and non-movably coupled to the one of the first or second connectors, and wherein the magnet unit may be movably coupled to the other one of the first or second connectors.

In some embodiments at least part of the first or second connector may be axially movable away from at least part of the other one of the first or second connector, while the attraction member and the magnet unit may not move axially relative to each other, to accommodate force spikes.

In some embodiments the at least part of the first or second connectors may be magnetically attracted to the magnet unit, and wherein the magnetic attraction between the at least part of the first or second connectors and the magnet unit may be configured to be overcome by a force spike when the assembly accommodates force spikes.

In some embodiments said closure valve may include a poppet positioned in said one of said first or second connectors, said poppet may be spring biased to said closed position, and wherein the other one of said first or second connectors may include an extension which engages said poppet to retain said poppet in said open position when said assembly is in said first configuration.

In some embodiments one of said first and second connectors may be fluidly coupled to a fuel dispensing nozzle for dispensing fuel into an automobile fuel tank, and wherein the other one of said first and second connectors may be fluidly coupled to a fuel pump.

In some embodiments the magnets may be generally shaped as rectangular prisms.

In some embodiments each magnet may have a longest dimension that is axially aligned and a second-longest dimension that is radially aligned such that each magnet is aligned with a radial line of the breakaway assembly in axial end view.

In some embodiments each magnet may be arranged at an angle relative to a radial line of <NUM> degrees or less, and wherein the polarity of the inwardly-facing surfaces of the magnets may alternate between adjacent magnets.

In some embodiments there may be exactly an even number of magnets.

In some embodiments each magnet may be arranged at an angle relative to a radial line of greater than or equal to <NUM> degrees and less than <NUM> degrees.

In some embodiments the magnet unit may includes a spacer that defines a plurality of channel portions, and each channel portion may closely receive one of the magnets therein.

In some embodiments the magnet unit may include a first portion and a second portion coupled to the first portion that together define the channel therebetween.

In some embodiments each magnet may have a longest dimension that is axially aligned and a second-longest dimension that may be generally circumferentially aligned.

In some embodiments the polarity of an inwardly-facing surface of the magnets may be the same for all of the magnets.

In some embodiments the magnets and channel may be arranged such that each magnet may have two points of contact with the channel, and a near-contact location that is spaced away from the channel, in a radial direction, less than about <NUM>% of the length of the magnet may be in a generally circumferential direction.

In some embodiments the at least part of the first or second connectors may be biased to a rest position by a biasing element, and may be configured to move axially to an actuated position when accommodating a force spike.

In some embodiments the biasing element may be fluidly isolated from the fluid path.

In some embodiments the biasing element may be at least one of a resilient member or a magnet.

In some embodiments the at least part of the first or second connectors may be an annular component that extends circumferentially entirely around the fluid path.

In some embodiments the at least part of the first or second connectors may be magnetically attracted to the magnet unit, and wherein the magnetic attraction between the at least part of the first or second connectors and the magnet unit may be configured to be overcome by a force of the force spike when the assembly accommodates a force spike.

In some embodiments the at least part of the first or second connectors may be magnetically attracted to the magnet unit by a force that is less than the magnetic attraction between the attraction member and the magnet unit when the assembly is in the first configuration.

In some embodiments the magnet unit may have two opposite axial ends, and wherein the magnet unit may has a stronger magnetic force at one axial end as compared to the other axial end.

In some embodiments the least part of the first or second connectors may be configured to be positioned adjacent to the magnet unit during normal operation of the assembly, and to move axially away from the magnet unit when the assembly accommodate a force spike.

In some embodiments the force spike may be at least one of a fluid line shock in the fluid path, or an impulse load applied by a user.

In some embodiments a force of a force spike required to cause the at least part of the first or second connectors to axially move may be less than the separation force.

In some embodiments the closure valve may be configured such that the closure valve does not move toward the closed position when the at least part of the first or second connectors moves to accommodate a force spike.

In some embodiments the at least part of the first or second connectors that is axially moveable may be an inner member of the one of the first or second connectors.

In some embodiments the at least part of the first or second connectors that is axially movable may be biased toward an axially inner position and may be configured to move away from the axially inner position, to an axially outer position, when accommodating a force spike.

In some embodiments the at least part of the first or second connectors that is axially movable may be axially movable relative to the closure valve when accommodating a force spike.

In some embodiments at least part of the other one of the first or second connectors may be axially movable relative to a remaining portion of the other one of the first or second connectors, or may be axially movable relative to the one of the first or second connectors, when the assembly is in the first configuration and while the closure valve remains open, to accommodate force spikes.

In some embodiments the at least part of the one of the first or second connectors and the at least part of the other one of the first or second connectors may be configured to accommodate force spike at least partially differing levels of force to provide staged force spike accommodation.

In some embodiments the at least part of the first or second connectors may be configured to move axially by a distance of at least about <NUM> (<NUM>/<NUM>) and less than about <NUM> (<NUM>/16inch) to accommodate force spikes.

Claim 1:
A breakaway assembly (<NUM>) comprising:
a first connector (<NUM>);
a second connector (<NUM>) releasably couplable to said first connector (<NUM>), wherein said assembly (<NUM>) is movable between a first configuration in which said first (<NUM>) and second (<NUM>) connectors are releasably coupled and together define a fluid path (<NUM>) through which fluid is flowable, and a second configuration in which said first (<NUM>) and second (<NUM>) connectors are not coupled together, wherein said assembly (<NUM>) is configured to move from said first configuration to said second configuration when a predetermined separation force is applied to said assembly (<NUM>);
a closure valve (<NUM>, <NUM>) positioned in one of said first (<NUM>) or second (<NUM>) connectors, wherein said closure valve (<NUM>, <NUM>) is configured to be in an open position when said assembly (<NUM>) is in said first configuration to allow fluid to flow therethrough, and to move to a closed position when said assembly (<NUM>) moves to said second configuration to generally block the flow of fluid therethrough;
an attraction member (<NUM>) coupled to one of the first (<NUM>) or second (<NUM>) connectors; and
a magnet unit (<NUM>) coupled to the other one of the first (<NUM>) or second (<NUM>) connectors, wherein the attraction member (<NUM>) and the magnet unit (<NUM>) are magnetically attracted to each other when the assembly (<NUM>) is in the first configuration to retain assembly (<NUM>) in the first configuration, wherein the magnet unit (<NUM>) includes a channel or channels (<NUM>, <NUM>) that includes a plurality of magnets or a magnet (<NUM>) received therein, wherein the magnets (<NUM>) are positioned at an angle other than perpendicular relative to a radial line of the breakaway assembly (<NUM>) in axial end view, and wherein a face corresponding to a pole of each magnet (<NUM>) lies in a plane oriented parallel to a central axis (A) of the assembly (<NUM>).