Patent Application
20170248271
The invention relates to the supply of fluid to a component. For example, the fluid may be a gas, or alternatively a liquid. More particularly, an aspect of the invention relates to a grease nipple and grease nipple coupler, and/or a fluid fitting and/or fluid coupler.
The purpose of such lubrication apparatus is to provide a convenient interface between a component which requires grease to be delivered to it, such as a bearing, etc and a pressurized grease supply, sometimes called a grease gun. Common pressures utilized range from 1.7 MPa (247 psi) to 40 MPa (5800 psi), or even higher in some specialized applications (e.g. up to 10,000 PSI). The use of such high pressures implies special safety considerations and means that the grease couplers and grease fittings used in lubrication apparatuses need to be highly resilient.
In use grease fittings, such as grease nipples, are attached to the component which requires greasing. The grease nipple provides an entry point for grease into the component. A grease applicator or grease coupler which is connected to the pressurized grease supply may then be coupled with the grease nipple, in order to supply the grease to the component through the nipple.
The most common existing form of fitting used is the hardened grease nipple. The grease nipple has a hardened ball which projects from the top of the fitting, which the coupler connects to. A one-way valve is located at the end of the projecting ball to prevent grease being released from the nipple.
A variety of different forms of couplers are used to couple with the grease nipple. These couplers either force grease into the nipple under pressure alone or may also have a needle to press down on the one-way valve mechanism. In either case, the grease pressure between the coupler and the nipple generates a force pushing the coupler away from the nipple. In order to overcome this separating force couplers and nipples are typically secured to each other when in use.
One type of coupler is the clamp-style coupler which has a number of steel jaws. These jaws pass around the head of the nipple then clamp around its base and prevent the coupler and nipple from separating under pressure.
The clamp style of applicator nozzle or coupler uses a number of hardened steel jaws, usually four, built into the end of the nozzle. When the applicator is forced over the nipple these jaws are spring loaded and move out of the way and then clamp on to the base of the grease nipple. This base is often not hardened. When the grease is forced into the nipple, the jaws are forced into the base of the fitting thus preventing the nozzle from being pushed off the fitting. This clamping action can include jamming and can make it hard to remove the applicator nozzle after the grease has been injected.
The tight clamping required and movement between the coupler and the nipple can result in wear and damage to the grease nipple. The tightly clamped jaws can be hard to remove, and further damage to the nipple can occur if the coupler is forced off of the nipple.
This wear and damage to the neck and head of the nipple can cause grease to leak, and even sever the head of the nipple. The release of high-pressure grease presents a significant safety risk, and involves time and cost in replacing the fitting.
A second common type of grease coupler is the slide-on coupler. This coupler features a collar which slides (side-on) over the neck of the nipple, and prevents the collar and nipple from separating under pressure as the collar is forced up on the base of the nipple's head. The collar is dimensioned to fit over the reduced neck of the grease nipple, but to be too small to be pulled over the top of the grease nipple.
In addition to causing wear to the nipple, as already discussed in relation to the clamping-style coupler, the slide-on coupler commonly provides a poor connection with the nipple and requires space around at least one side of the equipment around the grease nipple, so that the coupler may be properly aligned and slid onto the grease nipple.
Leaking between the nipple and coupler can falsely appear to an operator to be an indication of over-pressure, and can cause the operator to stop greasing before enough grease has been supplied to the component. This can lead to unintentional wear or even the failure of the component. Further, leaked lubricant can be difficult to clean, and result in additional time to complete the lubrication task and/or result in increased downtime of the machinery.
The dangers presented by high pressure grease, particularly where nipple heads have been severed, and the pressure has been allowed to escape, are well known. Serious injuries have been documented in these situations even when operators have been wearing protective equipment.
Other problems with current lubrication apparatus include the possibility of unequal pressures forming between the grease applicator nozzle and grease fitting which can cause more wear and tear, and the possibility of unwanted entry of impurities. Additionally unequal pressure or a build up of significant back pressure in the grease line of the grease fitting, can be a problem with current lubrication apparatus. For example, high back pressures can potentially cause the applicator nozzle to break or rupture the grease nipple, and the ball bearing within the grease nipple may shoot out like a bullet, and also potentially shoot grease back onto the operator. Existing lubrication apparatus also have an excessive number of parts (eg. up to ten or more), also resulting in high maintenance, increased cost of manufacture, and increased risk of failure.
In this specification, where reference has been made to external sources of information, including patent specifications and other documents, this is generally for the purpose of providing a context for discussing the features of the present invention. Unless stated otherwise, reference to such sources of information is not to be construed, in any jurisdiction, as an admission that such sources of information are prior art or form part of the common general knowledge in the art.
It is an object of the present invention to provide a fluid transfer apparatus and/or a lubrication apparatus and/or gas or liquid coupling apparatus, that overcomes or at least partially ameliorates some of the abovementioned disadvantages, or which at least provides the public with a useful choice.
In one aspect the invention broadly comprises a supply apparatus which is adapted to attach to a device that requires lubrication or the supply of fluid, comprising:
According to a further aspect the fitting channel includes at least one movable sealing means.
According to a further aspect the movable sealing means is located proximate to the or each first entry ports of the fitting channel.
According to a further aspect the sealing means is a resiliently mounted spherical ball.
According to a further aspect the fitting channel includes a first channel diameter portion leading to a second channel diameter portion, wherein the first diameter portions less than the second portion, defining a valve seat, and
According to a further aspect the or each entry port is a hole or a slot, and has a width of 1 to 1000 μm.
According to a further aspect there are entry ports in the form of a pair of parallel slots, each of which extends across either a majority, or substantially all, of the cross-section of the insertable section of the fitting.
According to a further aspect said insertable section defines an axis of insertion, and said entry ports are located in a side wall of said insertable section and are adapted to receive fluid in a direction laterally with respect to said axis.
According to a further aspect said lateral receiving direction is perpendicular to said axis.
According to a further aspect wherein said hole of said coupler defines a second axis of insertion, and said feed channel exits are located in a side wall of said hole, and are adapted to expel fluid in a direction lateral with respect to said second axis.
According to a further aspect said lateral expelling direction is perpendicular to said second axis.
According to a further aspect said insertable section of said fitting is a frustoconical shape, and said hole of said coupler is a complimentary frustoconical shape.
According to a further aspect said frustoconical shape is tapered less than 15° from an insertion direction.
According to a further aspect insertable section is generally cylindrical in cross section, and defines an insertion direction parallel to an axis of said generally cylindrical insertable section.
According to a further aspect said one or more feed channel exits open into one or more grooves extending around the inside side wall of the coupler.
According to a further aspect there are between 1-10 feed channel exits.
According to a further aspect there are six feed channel exits.
According to a further aspect the apparatus has no additional sealing requirements, and the hole in the coupler, and the insertable section of the fitting, being dimensioned to form a fluid tight seal when engaged.
According to a further aspect the fitting includes at least one circumferential groove located around the perimeter of the insertable section, said one or more entry ports communicating with said groove and leading to the fitting channel.
According to a further aspect a further sealing means in the form of at least one continuous flexible seal is located in the circumferential groove, leaving a peripheral gap there around, and with the flexible seal being sized to allow fluid to be forced there around through the one or more entry ports.
According to a further aspect the insertable section of the fitting includes a fluid sealing means to provide a fluid tight seal between the coupler and the fitting.
According to a further aspect the fitting includes a pair of parallel, continuous fitting sealing grooves, a first fitting sealing groove and a second fitting sealing groove, around the periphery of the insertable section of the fitting, and
According to a further aspect the coupler includes a pair of parallel continuous coupler sealing grooves, including, a third coupler sealing groove and a fourth coupler sealing groove, around the inside edge of the hole, and wherein
According to a further aspect the coupler is a generally elongate body defining a coupler axis, wherein fluid flow through the body is generally parallel to said coupler axis, and
According to a further aspect the coupler is a generally elongate body defining a coupler axis, wherein fluid flow through the body is generally parallel to said coupler axis, and
According to a further aspect said angle is 90°.
According to a further aspect the hole of the coupler includes at least one vent hole providing a pathway for an unwanted fluid such as air trapped between an end of the fitting and hole, adapted to allow the air to escape there from.
According to a further aspect the pathway extends from an end of said hole to an end of the coupler.
According to a further aspect the fitting includes an insertable section coterminous with a tightening section adapted to allow said fitting to be engaged by a tool and rotated, which is in turn coterminous with a threaded section at an opposite end of the fitting to the insertable section and adapted to allow the fitting to be engaged with a machine component.
In another aspect the invention broadly comprises an apparatus including a fitting, which is attachable to a device that requires lubrication or the supply of fluid, and a complementary coupler, which is connectable to a fluid reservoir, comprising:
According to a further aspect the circumferential groove may be provided with further continuous flexible seals.
According to a further aspect said insertable section defines an axis of insertion, and said entry ports are located in a side wall of said insertable section and are adapted to receive fluid in a direction laterally with respect to said axis.
According to a further aspect said lateral receiving direction is perpendicular to said axis.
According to a further aspect said hole of said coupler defines a second axis of insertion, and said feed channel exits are located in a side wall of said hole, and are adapted to expel fluid in a direction lateral with respect to said second axis.
According to a further aspect said lateral expelling direction is perpendicular to said second axis.
According to a further aspect said insertable section of said fitting is a frustoconical shape, and said hole of said coupler is a complimentary frustoconical shape.
In another aspect the invention broadly comprises a fitting, which is attachable to a device that requires lubrication or the supply of fluid, and is also attachable to a complementary coupler, which is connectable to a fluid reservoir, comprising:
According to a further aspect the fitting channel includes at least one movable sealing means.
According to a further aspect the movable sealing means is located proximate to the or each entry port of the fitting channel.
According to a further aspect the sealing means is a resiliently mounted spherical ball.
According to a further aspect the fitting channel includes a first channel diameter portion leading to a second channel diameter portion, wherein the first diameter portions less than the second portion, defining a valve seat, and the spherical ball is located in the second diameter channel portion to biasedly seal against said valve seat.
According to a further aspect the or each entry port is a hole or a slot, and has a width of 1 to 1000 μm.
According to a further aspect there are entry ports in the form of a pair of parallel slots, each of which extends across either a majority, or substantially all, of the cross-section of the insertable section of the fitting.
According to a further aspect said insertable section defines an axis of insertion, and said entry ports are located in a side wall of said insertable section and are adapted to receive fluid in a direction laterally with respect to said axis.
According to a further aspect said lateral receiving direction is perpendicular to said axis.
According to a further aspect said insertable section of said fitting is a frustoconical shape, and said hole of said coupler is a complimentary frustoconical shape.
According to a further aspect said insertable section is generally cylindrical in cross section, and defines an insertion direction parallel to an axis of said generally cylindrical insertable section.
According to a further aspect the fitting includes at least one circumferential groove located around the perimeter of the insertable section, said one or more entry ports communicating with said groove and leading to the fitting channel.
According to a further aspect a further sealing means in the form of at least one continuous flexible seal is located in the circumferential groove, leaving a peripheral gap there around, and with the flexible seal being sized to allow fluid to be forced there around through the one or more entry ports.
According to a further aspect the insertable section of the fitting includes a fluid sealing means to provide a fluid tight seal between the coupler and the fitting.
According to a further aspect the fitting includes a pair of parallel, continuous fitting sealing grooves, a first fitting sealing groove and a second fitting sealing groove, around the periphery of the insertable section of the fitting, and the first groove is above the or each entry port, and the second groove is below the or each entry port, and
In another aspect the invention broadly comprises an apparatus defining a coupler which is connectable to a fluid reservoir, and is connectable to a fitting, comprising:
According to a further aspect said one or more feed channel exits open into one or more grooves extending around the inside side wall of the coupler.
According to a further aspect there are between 1-10 feed channel exits.
According to a further aspect there are six feed channel exits.
According to a further aspect the coupler includes a pair of parallel continuous coupler sealing grooves, including, a third coupler sealing groove and a fourth coupler sealing groove, around the inside edge of the hole, and wherein
According to a further aspect the coupler is a generally elongate body defining a coupler axis, wherein fluid flow through the body is generally parallel to said coupler axis, and
According to a further aspect the coupler is a generally elongate body defining a coupler axis, wherein fluid flow through the body is generally parallel to said coupler axis, and
According to a further aspect said angle is 90°.
According to a further aspect the hole of the coupler includes at least one vent hole providing a pathway for an unwanted fluid such as air trapped between an end of the fitting and hole, adapted to allow the air to escape there from.
According to a further aspect the pathway extends from an end of said hole to an end of the coupler.
According to a further aspect said hole of said coupler defines a second axis of insertion, and said feed channel exits are located in a side wall of said hole, and are adapted to expel fluid in a direction lateral with respect to said second axis.
According to a further aspect said lateral expelling direction is perpendicular to said second axis.
According to a further aspect said hole of said coupler is a frustoconical shape.
According to a further aspect said coupler has no additional sealing means within the hole in the coupler.
According to a further aspect the hole of the coupler includes at least one vent hole providing a pathway for an unwanted fluid such as air trapped between an end of the fitting and hole, adapted to allow the air to escape there from.
According to a further aspect at least one vent hole is large and/or numerous, such that a portion of said coupler upstream of said feed channel is mostly open to the atmosphere.
According to a further aspect said coupler is skeletal, and said feed channel extends through a limb of said skeletal structure.
According to a further aspect the pathway extends from an end of said hole to an end of the coupler.
In another aspect the invention broadly comprises a fitting assembly for providing gases from a gases supply, to a component to be pressurised or inflated, comprising:
According to a further aspect said valve core is retained in said hollow of said valve body, such that it can be moved between a first position wherein said valve core is at least mostly within set valve body, and a second position wherein said valve core is entirely within said valve body.
According to a further aspect said valve core is biased towards a said first position.
According to a further aspect said valve core includes sealing means between an outer surface of said valve core, and an inner surface of said hollow of said valve body.
According to a further aspect said sealing means comprises a pair of flexible continuous seals, one of which is located above the level of said at least one entry port, and the other of said seals is located below the level of said at least one entry port.
According to a further aspect said hollow body is blocked at one end, being said second end.
According to a further aspect said valve body includes sealing means between an outer surface of said valve core and an inner surface of said hollow of said valve body.
According to a further aspect said sealing means comprises a pair of flexible continuous seals, one of which is located above the level of said at least one entry port, and the other of said seals is located below the level of said at least one entry port.
According to a further aspect said valve body is adapted to be fitted to said component to be inflated or pressurised, such that said exit communicates with said component.
In another aspect the invention broadly comprises a coupler adapted to receive a fluid from a fluid supply, and to couple with a fitting comprising:
According to a further aspect said transverse direction is perpendicular.
According to a further aspect said one or more exit ports open into one or more grooves extending around an outer surface of said projection.
According to a further aspect there are between 1-10 exit ports.
According to a further aspect there are 2 exit ports.
According to a further aspect the coupler includes a pair of parallel continuous coupler sealing grooves, including, a first coupler sealing groove and a second coupler sealing groove, around the outer surface of said projection, and wherein the first groove is located above the exit ports, and the second groove is below the exit ports, and
According to a further aspect said receiving recess in said outlet end of said body further defines an outer wall extending around said receiving recess.
According to a further aspect said outer wall projects beyond an outermost extent of said projection.
In another aspect the invention broadly comprises a fluid transfer apparatus comprising:
According to a further aspect when in an engaged position, said exit port is able to communicate with said entry port.
In another aspect the invention broadly comprises a nipple for passing grease to a component to be lubricated, and which, when in use, is also attachable to a coupler which is connected to a grease supply, the nipple comprising:
In another aspect the invention broadly comprises a coupler for providing grease from a grease supply to a grease nipple, the coupler comprising:
In another aspect the invention broadly comprises a fitting substantially as described herein, and with reference to any one or more of the drawings.
In another aspect the invention broadly comprises a coupler substantially as described herein, and with reference to any one or more of the drawings.
In another aspect the invention broadly comprises a fluid transfer apparatus substantially as described herein, and with reference to any one or more of the drawings.
In another aspect the invention broadly comprises a grease nipple substantially as herein described, and with reference to any one or more of the drawings.
In another aspect the invention broadly comprises a grease nipple coupler substantially as herein described, and with reference to any one or more of the drawings.
The invention consists in the foregoing and also envisages constructions of which the following gives examples only.
The term “comprising” as used in this specification and claims means “consisting at least in part of”. When interpreting each statement in this specification and claims that includes the term “comprising”, features other than that or those prefaced by the term may also be present. Related terms such as “comprise” and “comprises” are to be interpreted in the same manner.
These and other features and characteristics of the present invention, as well as the method of operation and functions of the related elements of structures and the combination of parts and economics of manufacture, will become more apparent upon consideration of the following description with reference to the accompanying drawings, all of which form part of this specification, wherein like reference numerals designate corresponding parts in the various figures.
Referring to
The apparatus 1 comprising an applicator nozzle or coupler 2 adapted to provide a source of lubricant, and a fitting 3 adapted to receive the lubricant to provide to a device where required. The coupler 2 can be provided as part of a grease gun connectable to a fluid reservoir, and the fitting 3 can be provided by a grease nipple type arrangement.
Referring to
The fitting 3 includes, at one end, an insertable section which includes cylindrical section 14, coterminous with a tightening section 15, which is in turn coterminous with a threaded section 16 located at the other end.
Wholly within the fitting 3 is a fitting channel 17, this fitting channel 17 has one or more entry ports 18 through the side of the cylindrical section 14 of the fitting 3, and an exit 21 through an end of the fitting 3 distal to the cylindrical section 14. The or each entry port 18 may be a hole (of circular or other cross-section) of approximately 1 to 1000 μm in width, or may be slots, functioning as an entry for the grease sourced from the exit 8 of the coupler 2.
Some alternative examples of different configurations of entry ports 18 are shown in
Referring back to
Inside fitting channel 17 there is a sealing means 41. In this example the sealing means 41 is a spherical ball retained and operated as a seal in a standard manner known in the art. E.g: with a ball bearing movably held by a spring (not shown) in a large diameter channel 17 leading to a narrower diameter entrance portion, defining a seat 6.
The threaded section 16 engages with a matching threaded hole (not shown) in the device (not shown) to be supplied with grease. The threaded section 16 connecting and, when tightened correctly, providing a fluid tight seal between the fitting 3, and the device (not shown).
The tightening section 15 is hexagonal in cross section when viewed along the centreline of the fitting 3, and preferably has its entire periphery outside the diameter of the cylindrical section 14, to allow easy access by a spanner. The tightening section 15 is further dimensioned to allow the force required to reversibly connect the fitting 3, to the device (not shown), to be applied without distortion or failure of the fitting 3.
Alternatively, it will be appreciated that the tightening section 15 may comprise a pair of opposed parallel flat surfaces, or any other shape suitable for mating with a spanner, or spanner like tool.
The fitting 3 further includes a first sealing groove 22, and a second sealing groove 23; the first sealing groove 22 is located above the level of each entry port 18, the second sealing groove 23 is located below the level of each entry port 18. Within each sealing groove 22, 23 is a continuous flexible sealing member, such as for example at least one O-ring or flexible gasket 24. The O-ring 24 is dimensioned to form a fluid tight seal against the side wall 9 of the coupler 2.
It will be appreciated that under pressure of fluid transferring between the coupler 2 and fitting 3 (described later), the O-rings will be pressed into a sealing state.
To assemble the lubrication apparatus 1, the blind hole 4 in coupler 2 is engaged with the cylindrical section 14 of the fitting 3. The coupler 2 is pushed on to the fitting 3 coming to rest when the coupler end 26 contacts the top face 29 of the tightening section 15.
In this engaged position, each feed channel exit 8 is aligned with the or each entry port 18, as shown in
In order to facilitate engagement, it will be appreciated that blind hole 4 is shaped to substantially correspond with the shape of the insertable portion 14 of the fitting 3. In this respect, it is envisaged that a large number of possible complementary shapes may be adopted. The described embodiments disclose substantially cylindrical and/or conical shapes for convenience, although these shapes are preferred due to their circular cross sections, which suit standard circular O-rings.
However, the person skilled in the art will readily be able to adapt various shapes and provide suitable flexible gasket's to match. For example, the complementary cross-sectional shapes of the blind hole 4 and insertable portions 14 respectively, may be: oval, elliptical, polygonal (with sharp or rounded corners), star shaped (with sharp or rounded corners), Reuleaux polygons, quatrefoil, pentalobe etc.
During the engagement of the coupler 2, with the fitting 3, any fluid trapped between a top 30 of the fitting 3, and a blind end 31 of the blind hole 4, can escape via one or more vent holes 25 in the coupler 2.
The or each vent hole 25 routes the grease to an exterior surface of the coupler 2 so that any trapped fluid can vent to the atmosphere. For example, as shown in
The or each vent hole 25 also allows air to be sucked in during the removal of the coupler 2 from the fitting 3. Alternatively, at least one vent hole 25 may be located either in the side of the coupler 2.
In a further embodiment (described later in shown in
In use, as shown in
It will be appreciated that groove 10 (if provided), allows the apparatus to function when the radial alignment of the exit 8, with entry port 18, is not perfect.
The grease from the grease delivery system (not shown, but including a reservoir and connected directly or indirectly, to the coupler) is pressurised and forced through the feed channel 5, and into the feed channel exit 8. The pressure of the grease increases in the feed channel exit 8 until the spherical ball 41 is moved out of the way, opening the seal, and the grease then flows through the fitting channel 17 out of the second exit 21, and into the device to be lubricated (not shown). It will be appreciated that incompressible fluids (or at least nearly incompressible) will be easily able to move the ball valve 41.
In a further alternative variation, as shown in
A first sealing groove 32, and a second sealing groove 33, are provided around the inside circumference of the blind hole 4, perpendicular to the centreline of the blind hole 4. The sealing grooves 32,33 are located so that when the coupler 2 is in use, (as shown in FIG. 4), the first sealing groove 32 is above the or each first exit 8 in the fitting, and the second sealing groove 33 is below the or each first exit of the fitting.
Within each sealing groove 32,33 is a continuous flexible sealing member such as for example sealing means in the form of an O ring or gasket 36, which is dimensioned to form a fluid tight seal against the outside of the cylindrical section 14 of the fitting 3.
In a further alternative variation, as shown in
This configuration requires close tolerances between the interior surface of blind hole 4 in the coupler 2, and the exterior surface of the cylindrical section 14 of the fitting 3, to form a fluid tight seal between the coupler 2, and fitting 3. This embodiment may be particularly suitable to use with for example, a ceramic coupler 2, for example, as ceramic parts can be manufactured to very close tolerances.
In still further alternative variations, as shown in
The feed channel exit 8, and entry ports 18, (or at least the terminal and initial portions thereof respectively) are oriented to be substantially perpendicular to the coupling direction 7, thereby minimising pressurised fluid forces parallel to the coupling direction, which would otherwise tend to try and separate the coupler 2 from the fitting 3.
In use, the grease flowing as shown by the arrows in
In particular, the coupling direction in which the insertable portion of fitting 3 couples with the coupler 2, is at least approximately perpendicular, to the direction of flow of lubricant from the coupler 2 to the fitting 3. That is, at least the terminal (last) portion of feed channel exit 8 is at least approximately perpendicular to the coupling direction, and at least the initial (first) portion of the entry port 18, is also at least approximately perpendicular to the coupling direction.
In practice, it has been found that it is not always necessary for the exit 9, or entry ports 18 to be actually geometrically perpendicular. What is important is that they mate in a generally lateral or transverse direction, so that the respective ports are located on the side of the fitting 3, and the coupler mates with the side ports so that grease is forced along the passageway, rather than against a surface causing a separation force between the coupler 2, and fitting 3.
However, alternatively the exit 9, and/or entry ports 18 may be actually geometrically perpendicular.
A further embodiment is illustrated in
As shown in
In this embodiment, the coupling direction in which the insertable portion of fitting 3 couples with the coupler 2, is also at least approximately perpendicular, to the direction of flow of lubricant from the coupler 2 to the fitting 3. That is, at least the terminal (last) portion of feed channel exit 8 is at least approximately perpendicular to the coupling direction, and at least the initial (first) portion of the entry port 18, is also at least approximately perpendicular to the coupling direction.
Alternatively, the entry ports 18 and/or the channel exits 8 are at least lateral or transverse, to the insertion direction.
Accordingly, forces opposing the coupling direction generated by the high-pressure lubricant are still significantly reduced, because the high-pressure lubricant does not press against a large area of the tapered surface of the insertable portion 13.
In this respect, it is preferred that the taper (shown in
In each of these embodiments, the or each entry port 18 is a substantially round hole of approximately 1 mm in diameter, and is sealed by a sealing means 41. However, it will be appreciated that the particular application for which the apparatus is used may call for smaller, or much larger apparatus. Accordingly, the above examples are typical of a ‘standard’ sized coupler 2, and fitting 3.
The sealing means 41 is preferably a movable spherical ball 41 retained and operating as a seal in a standard manner known in the art. However, it will be appreciated that other valve mechanisms may be used to allow high-pressure fluid into the fitting, while preventing egress of fluid after the filling operation is completed.
Further, it will be appreciated that the seal 41, as illustrated is only one possible example. In alternative variations, the seal 41 may be located adjacent entry port 18 as shown in
Alternatively, the seal 41 is preferably located approximately as illustrated, or even further towards the lower end of fitting 3. An advantage of such a configuration is the ability to seal even if the cylindrical portion 14 is broken off fitting 3.
With reference to
The alternative variation of
The further alternative variation of
The further alternative variation of
It will be appreciated that the spatial arrangement and cross-sectional shape of the entry port(s) 18, and corresponding feed channel exits 8 (of the coupler 2), need not necessarily match exactly. All that is necessary is that they intersect so that the fluid can flow from at least one coupler exit 8, into at least one fitting entry port 18.
Similarly, it will be appreciated that the various combinations of seal arrangements 24 can be applied to each of the coupler 2 and/or fitting 3 shapes in a similar way as described above in order to provide:
As noted previously, embodiments including one or more grooves 10, allow some radial misalignment, between the coupler two and fitting 3, without significantly affecting performance.
Referring to
Referring to
The feed channels 605, provide paths for the grease to flow from a grease delivery system (not shown) to one or more feed channel exits 608. Multiple feed channel exits 608 may be provided, or the feed channel exits may be linked in one or more continuous grooves around the surface of the side wall 609.
The feed channels 605, need to provide a path between the grease delivery system and the or each feed channel exits 608, but it will be apparent to one skilled in the art this may be achieved by many different configurations of feed channels 605.
One embodiment of the feed channels 605 is shown in
The fitting 603 of
Wholly within the fitting 603 is a fitting channel 617, and this fitting channel 617 has one or more entry ports 618 through the side of the cylindrical section 614 of the fitting 603, and an exit 621 through an end of the fitting 603, distal to the cylindrical section 614.
The, or each entry port 618 includes a hole (of circular or other cross-section) of 1 to 1000 μm in width, or may be vertical or horizontal slots. Examples of different configurations of entry port configurations 618 are shown in
The entry ports 618 may be sealed by a sealing means, such as a spherical ball 641, retained by spring 642 and operating as a seal in a standard manner known in the art.
The configuration of the entry ports 618 of the fitting 603 will be complementary to the configuration of the feed channel exits 608 of the coupler 602, as described below.
In the embodiment shown in
Circumferential groove 640 may receive a continuous flexible sealing member such as for example at least one O-ring, or gasket 624b. The purpose of this O-ring 624b, is to prevent, (or at least reduce), any debris from entering the ports 618.
In use, the fluid or grease is pushed under pressure from the feed channel exits 608 of the applicator nozzle 602, onto the O-ring located in channel or groove 640, to squeeze around a peripheral gap between the O-ring and channel 640, leading to entry port 618 located within the groove (640)
The cylindrical section 614 is dimensioned to be a close fit inside the blind hole 604 in the coupler 602. In
Inside fitting channel 617 is a sealing means 641. The sealing means 641 is a spherical ball retained and operated as a seal in a standard manner known in the art, for example, as a spring-loaded ball (by spring 642).
The fitting channel 617 includes a first channel diameter portion and second channel diameter portion, whereby the first channel diameter portion is less than the second channel diameter portion. The first channel diameter portion is located close to the entry port(s) 618, and the ball 641 is located within the second channel diameter portion to be held against a seat portion 606, to seal the fitting channel unless grease is forced there against the ball 641.
The threaded section 616 engages with a matching threaded hole (not shown) in the device (not shown) to be supplied with grease. The threaded section 616 connecting and, when tightened correctly, providing a fluid tight seal between the fitting 603, and the device (not shown).
The tightening section 615 is hexagonal in cross section when viewed along the centreline of the fitting 603, and is dimensioned to allow the force required to reversibly connect the fitting 603 to the device (not shown), to be applied without distortion or failure of the fitting 603.
As seen
To assemble the apparatus 601, the blind hole 604 in the coupler 602 is engaged with the cylindrical section 614 of the fitting 603. The coupler 602 is then pushed on to the fitting 603, coming to rest when the top 630, of the fitting 603, contacts the blind end 631 of the blind hole 604. In this engaged position, the or each feed channel exit 608, is aligned with the or each entry port 618.
During the engagement of the coupler 602, with the fitting 603 any fluid trapped between the top 630, of the fitting 603, and a blind end 631 of the blind hole 604, can escape via one or more vent holes 625, in the coupler 602, as shown in
The
Ready for use, as shown in
The grease from the grease delivery system (not shown, but including a reservoir and connected directly, or indirectly, to the coupler) will be pressurised and forced through the feed channel 605, and into the feed channel exit 608. The grease will be passed around the edges of the O-ring 624b, and into channel 640, before entering entry ports 618. The pressure of the grease will increase in the feed channel exit 608, until the spherical ball 641 is moved out of the way, opening the sealing means and allowing grease past ball 641. Grease can flow through the fitting channel 617, out of exit 621, and into the device to be lubricated (not shown).
The various embodiments described above include a number of different features, and it will be apparent to one skilled in the art that they may be combined in combinations other than those specifically described, in order to achieve the object of the invention, and without departing from the spirit and scope of the present invention. All such modifications and variations as would be apparent to persons skilled in the art fall within the broad scope and ambit of the invention.
The tightening section 15, 615, and threaded section 16,616 can be as long, or have a pitch as required. Similarly for the coupler 2, 602 this can be as long as necessary and have an outer tightening portion to allow a fastening tool to rotate the coupler 2, 602 onto whatever it is to fluidly connected to eg an applicator or grease gun or a fluid line etc.
The number of outlets for vent holes 25,625 can be any number, pattern and diameter and be placed wherever required. The number, size and spacing of the grooves 22,23, 622, 623, 32, 33 can be varied to suit requirements and similarly for the gasket 24, 624 which can be placed on the fitting 2, and/or in the blind hole 4. The size and shape of the feed channel 5 can also be varied.
It will also be understood that where a product, method or process as herein described or claimed and that is sold incomplete, as individual components, or as a “kit of Parts”, that such exploitation will fall within the ambit of the invention.
In yet further options the fitting 3 can also include a dust cover member (not shown), like for example being in the form of a cylindrical member having an internal recess portion shaped to mirror the outward shape of the insertable section 14, and optionally extend to cover the tightening section (15). In this example the dust cover can be made of plastics or silicon.
The fluid supply end is provided with means to allow removable connection to a supply of lubricant or whatever fluid is being used by the apparatus. In this example the means includes a cylindrical recess 707 with a peripheral inner thread. The main body of the coupler 702, is a substantially square shaped cross-section, with a flat end face at the discharge end 701.
A grease feed channel 705 extends through the body of the coupler from the grease supply 707, to the grease channel exit 708. In this embodiment the receiving portion 704 of the coupler 702, extends entirely through the body of the coupler, thus eliminating the need for vent passages to allow trapped air to escape. Further, this embodiment may allow the coupler 702 to be fitted to a fitting from either side. Alternatively, the nipple receiving portion 704 may be a blind hole, as described previously.
In use, the insertable portion of a grease nipple 14 may be inserted into the receiving portion 704. Grease may be then passed from the grease supply, through the grease channel 705, and out the grease channel exit 708, wherein it passes into the inlet ports 18, of the grease nipple fitting 3. It will be appreciated that the feed channel exit ports 708, may be complimentary shaped, to operate with any of the grease nipple fittings 3 described in this specification.
The outlet port 708 of the grease channel of the coupler 702 may consist of a circumferential ring 703 around the nipple receiving portion 704. This arrangement allows grease to pass to the inlet port 18 of the nipple regardless of the circumferential orientation of the receiving inlet ports on the nipple (as shown by arrows in
An additional alternate embodiment of a coupling apparatus 800, that is particularly suited for gases transfer, comprises a coupler 802, and fitting 803. For convenience, these embodiments described below will be referred to generally as a pneumatic coupling apparatus, comprising a pneumatic fitting and a pneumatic coupler, however it will be appreciated that such apparatus may also find use in the transfer of other gases, and/or fluids.
The pneumatic coupling apparatus 800, and operation of the apparatus 800, is illustrated in
The pneumatic fitting assembly 803 comprises an elongate hollow body 810, valve core 820 and a valve base 830. The fitting 803 comprises a hollow body with a first end 816 which is adapted to be connected to a component to be inflated or pressurized (not shown), and a second coupling end 817, which is adapted to be connected to the coupler 902 (described in more detail later).
It is envisaged that this coupling apparatus is particularly suited to applications where a component needs to be charged or filled, such as (but not limited to) pneumatic tyres, refrigeration systems etc.
The hollow body 810 preferably has three stepped internal diameters 812a, 812b and 812c, where each successive portion is of a smaller diameter, for receiving and retaining the valve core 820 within.
One or more air channels 813 are located in the wall of body 810. An inlet end of the air channels 813 are fluidly connected to inlet ports 818. The other (outlet) end of the one or more air channels 813, terminate in the component to be inflated or pressurised such that pressurised gases flowing through channels 813 can flow into the component.
The air valve core 820 is located within the hollow section 812. The core 820 preferably has a generally cylindrical shape with a lower end 821 of a smaller diameter, to allow spring 84 to pass around the lower end 821. Additionally the core 820 has one or more grooves 822, 823 in it to accommodate one or more sealing gaskets, such as o-rings 814.
A pressure relief channel 827 may additionally be located through (e.g. through the centre) the air valve core 820. The pressure relief channel 827 can allow gasses from below the air valve core 820, in the hollow sections 812b and 812c, to escape as the valve core slides downwards.
Core 820 preferably includes a shoulder 824 of a larger diameter, provided to contact the interface between the two hollow body parts 812b and 812c. This feature provides a positive stop, retaining the valve core 820 within the body 810.
The valve base 830 is dimensioned to fit snugly inside the widest part 812a of the hollow valve body 812, and retains the valve core 820 and spring 804 assembly within the valve body 810.
The assembly 803 includes a spring 804 (or other biasing means) located between the valve base 830, and the valve core 820. The spring 804 biases the valve core 820 into an upper (closed) position, to ensure the entry ports 818 are sealed, thereby preventing pressurized air in the component to be pressurised and or inflated from escaping.
As illustrated particularly in
In order to displace the valve core 820 downwards (and preferably provide a seal to the end 817 of the valve), fitting assembly 803 is coupled with a specially adapted coupler 902.
The air coupler 902 has a first end which is connected to the air valve assembly and a second end which is to be connected to the pressurized air supply (not shown).
The first end of the air coupler 902 which is able to be connected to the air valve assembly 803 has a projection 901 from its centre. The projection is sized to fit snugly into the narrowest hollow portion 812c of the air valve body 810, to displace the air valve core 820 downwards.
An external wall or hollow shell of material 907 preferably extends around the outside of the first end of the air coupler 902, defining a receiving area 904. The receiving area 904 is sized to snugly receive the end 817 of the air valve body 810.
In some configurations, the wall 907 may extend below the extent of projection 901. In this way the coupler 902 can be aligned onto the end of fitting 803, prior to the projection 901 engaging the valve core 820. This feature protects the projection 901 and/or valve core 820 from damage during alignment.
In a further variation, the wall 907 (or body of fitting 810), may be provided with features to provide a friction fit. Preferably, a friction fit is sufficient to resist the coupler 902 and fitting 803 from being pushed apart by the force of spring 804. For example the features may be surface textures, coatings or o-rings, or any other suitable method.
Within the air coupler 902 is an air delivery channel 905. The air channel 905 extends from the end connected to the pressurized air supply, through the projection 901. The air channel 905 terminates in one or more outlet ports 908, located on the sidewalls of the projection 901. The terminal portion of the outlet ports 908 are transverse to the direction in which the air coupler 902, and air valve assembly 803 couple together.
The location of the outlet ports 908 of the air channel 905 on the side walls of the projection 901, are such that when the coupler 902, and air valve assembly 803 are coupled together, the outlet ports 908 of the air coupler 902 correspond with the inlet ports 818 to the air channel 813, of the air valve assembly 803.
When the air coupler 902 and air valve assembly 803 are coupled together, the air channels 813 and 905 are in fluid communication, such that air may be passed from the pressurized air supply (not shown) to the component to be pressurized, as illustrated by arrows 911.
The projection 901 may incorporate one or more grooves 932, on either side of the outlets 908, in order to ensure a seal between the air coupler 902 and air valve assembly 803 when the two parts are coupled together. Preferably these grooves 932 our provided with gaskets or o-rings 936.
It will be appreciated that the pneumatic coupling apparatus 800, shares many common features with the lubrication apparatus 1 described earlier. The main difference between these two embodiments, is the coupler 902 is adapted to directly engage the valve mechanism, to open the fluid pathway between components. This variation enables the pneumatic coupler apparatus 800, to be particularly suited to the delivery of gaseous fluids under pressure.
According to a further variation, the arrangement of the gaskets 936, could be associated with the valve fitting 803, or a combination of the valve fitting 803 and the coupler 902.
Air Coupler with Venting
In an alternative embodiment a gases supply apparatus comprised of a nipple or fitting 1100 and fluid coupler 1200 are provided, and described with reference to
This embodiment is particularly suited to gases supply apparatus, for example for connection to an air supply line. Accordingly, the coupling between the coupler and fitting is more permanent (although separable) and needs to be retained throughout operation.
The nipple 1100 is to be attached to a component to which pressurized gas, for example air, is to be passed, while the air coupler 1200 is to be connected to a supply of pressurized air (not shown). When the nipple 1100 and air coupler 1200 are coupled together, pressurized air is allowed to pass from the pressurized air supply, through the components and into the component which requires pressurized air.
In this embodiment, the nipple 1100 is similar to that described earlier with reference to
Further, it is envisaged that a retaining means (not shown) of any suitable type is employed, to retain the coupler 1200 on the fitting 1100, during use. For example, in the industry there are many known retaining arrangements employed. Any suitable example may be adapted for present purposes, such as clip(s), collars, threaded fittings, hinged clamps etc.
The air coupler 1200 is particularly adapted to high pressure applications that also require high volumes of gases delivery such as jack hammers, sand/grit blasting and mining applications such as drilling etc. In these high-volume applications, there are additional safety considerations.
The air coupler 1200 has a first end 1201 which is to be attached to the pressurized air supply (not shown). The second end 1202 has a receiving portion 1203 formed in it, which is adapted to receive a part of the nipple 1100.
Within the body of the air coupler 1200 are provided one or more air channels 1204. A first end of the air channels 1204 terminate at the connection to the pressurized air supply on the first end 1201. The other end of the one or more air channels 1204 terminate in one or more outlet ports 1205 located on the side wall of the receiving portion 1203.
As described with respect to previous embodiments, the outlet ports 1205, provide pressurised fluid into the receiving portion in a direction that is perpendicular (or at least lateral, or transverse) to the coupling direction between nipple 1100 and coupler 1200, as shown in
The one or more outlet ports 1205 may comprise a circumferentially arranged set of individual outlet ports or may include a continuous groove around the circumference of the receiving portion 1203.
During decoupling of the nipple 1100 and the air coupler 1200, it is possible that there may be residual air under high pressure in the air channel 1204. Additionally, it may be possible that during either the coupling or decoupling of the components, the pressurized air supply may be continuously supplying pressurized air.
As the components couple and/or decouple, the release of this pressurized air may cause forces to be exerted on different surfaces of the components. In particular, the release of large volumes of pressurized air through the outlet ports 1205, when the components are being decoupled, may cause high forces to be exerted on either or both of the end face of the nipple 1100, or the sides of the void 1206. These forces they act to push the nipple 1100 and air coupler 1200 apart, rapidly.
When high pressures are combined with large volumes, this additional decoupling force could cause the components to be violently forced apart from one another. This presents a significant safety risk to an operator of the air supply apparatus, and/or others in the vicinity.
Accordingly, this variation of the air coupler 1200, incorporates safety features to reduce or eliminate the risks due to high volume and high pressure release when coupling, or decoupling. These features provide means for redirecting, or evenly venting high pressure air which is released from the coupler 1200, in opposing directions thereby neutralising the thrust.
The void 1206 is located at the base of the receiving portion 1203. In the preferred embodiment at least one side of the void 1206 is open to the atmosphere, providing a large exhaust pathway for any gases vented from the decoupled or partially decoupled air coupler outlet ports 1205.
It is preferable that any very high pressure gases is intended, have the opportunity to evenly dissipate in a balanced manner. That is, the gases venting forward of the coupler 1200 (as shown by arrows 1300) are not substantially less inhibited than gases venting rearward (towards end 1201, as shown by arrows 1301), in order that the venting gases, can vent evenly, thereby reducing the tendency to propel the coupler 1200 away from the nipple 1100.
Accordingly, it is preferred that the void 1206 is as large as practicable, resulting in the coupler 1200 being skeletal only around void 1206, while it is preferred that the receiving portion 1203 is a complete circumferential ring. In these alternative embodiments, the air channels 1204 pass through the arms of the skeletal portion of coupler 1200.
The back surface of the void 1206 may also be substantially curved or notched so as to direct any high pressure gasses through the one or more openings on the sides of the void.
In an alternate embodiment the void 1206 may comprise a very large volume space with closed sides. The void 1206 in this embodiment would be of a sufficient volume to allow any residual high pressure gases to dissipate pressure but would significantly increase the size of the, thus reducing or eliminating any pressure-induced decoupling of the nipple 1100 and coupler 1200. Closing off the void 1206 from the surroundings would decrease the opportunities for dirt or other contamination to enter the receiving portion 1203, but would significantly increase the size of the coupler.
In a further alternate embodiment, the void 1206 may comprise a space with partially closed sides and large bore pressure relief channels. These pressure relief channels would pass through the body of the air coupler 1200 and vent to the atmosphere.
It is envisaged that the fittings, and couplers described in this specification may be manufactured from a number of different materials, and by any suitable manufacturing technique.
For example, the components are preferably metallic, and most preferably a corrosion resistant metal such as stainless steel. However, other materials such a brass, mild steel, ceramic, polymer or fibre reinforced plastic may also be used. It will be appreciated that the particular application may influence the material choice preferred.
Similarly, the manufacturing technique preferred may also depend on the material selected. For example, the components may be machined in a lathe and/or mill, moulded, cast, 3D printed, or shaped by any other suitable manufacturing technique (or combination thereof).
For purposes of the description hereinafter, the terms “upper”, “lower”, “right”, “left”, “vertical”, “horizontal”, “top”, “bottom”, “lateral”, “transverse”, “longitudinal”, “side”, “front”, “rear” and derivatives thereof shall relate to the invention as it is oriented in the drawing figures. However it is to be understood that the invention may assume various alternative variations, except where expressly specified to the contrary. It is also to be understood that the specific devices illustrated in the attached drawings, and described in the following specification are simply exemplary embodiments of the invention. Hence specific dimensions and other physical characteristics related to the embodiments disclosed herein are not to be considered as limiting.
| Number | Date | Country | Kind |
|---|---|---|---|
| 700550 | Sep 2014 | NZ | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/IB2015/057467 | 9/30/2015 | WO | 00 |
