CN117396697A

CN117396697A - Quick lock release coupling

Info

Publication number: CN117396697A
Application number: CN202280038447.0A
Authority: CN
Inventors: 塞巴斯蒂安·特伦布莱; 米歇尔·泰隆
Original assignee: Taimi R&D Inc
Current assignee: Taimi R&D Inc
Priority date: 2021-05-05
Filing date: 2022-05-03
Publication date: 2024-01-12

Abstract

A quick release coupling for providing a connection between a pair of hydraulic lines is provided. The coupling includes a male member having a fluid conduit therethrough, and the male member includes a shank portion adapted to engage a first hydraulic line. The handle portion has a first port for establishing fluid communication between the first hydraulic line and the fluid conduit. The shank portion also has a limiting mechanism adapted to engage the first hydraulic line and prevent rotational and axial movement of the male member relative to the first hydraulic line. The coupling further includes a coupling adapter connectable to the male member and having a fluid passage therethrough adapted for fluid communication with the fluid conduit. The coupler adapter is adapted to engage the second hydraulic line and has a second port for establishing fluid communication between the second hydraulic line and the fluid passage.

Description

Quick lock release coupling

Technical Field

The present invention relates generally to couplings and, more particularly, to quick lock release couplings for hydraulic lines.

Background

Several types of couplings are used in the fluid transfer industry. For example, even though the application and some constructions are similar to other known couplings, a push-to-connect connector or "quick release coupling" is different. Quick release couplings, which are widely used in pneumatic industry and low pressure applications, are not designed for high pressure applications, such as for transferring fluids on heavy machinery where pressurized fluid is flowing and heavy machinery where torsional constraints exist. For example, most hydraulic lines composed of braided or intertwined metal wires or synthetic plastic materials are very sensitive to torsional constraints.

A rotational coupling is a component that enables two or more hydraulic lines to be interconnected axially or angularly and reduces torsional constraints that may affect their physical integrity or internal structure. The quick release coupling is typically formed by a male connector having a groove around its periphery allowing the ball bearings of the female connector to be trapped in the groove. Thus, axial movement is eliminated while the assembly is free to rotate. It is therefore similar in every respect to a rotary joint consisting of one or more rows of balls and seals. The pressurized hydraulic fluid, along with the rotation of known rotary joints and rotary couplings, accelerates wear and tear of various seals within the coupling, which requires frequent maintenance, repair and replacement.

Disclosure of Invention

According to one aspect, a quick release coupling is provided for providing a connection between a first fluid line provided with a female part comprising a ball bearing assembly and a second fluid line. The quick release coupling includes a male member having a fluid conduit therethrough and comprising: a body portion having an inner surface at least partially defining the fluid conduit; and a shank portion extending from the body portion and adapted to engage the female portion of the first fluid line, the shank portion having a shank portion port adapted to establish fluid communication between the first fluid line and the fluid conduit, the shank portion including a limiting mechanism adapted to engage the ball bearing assembly and prevent rotational and axial movement of the male member relative to the first fluid line when engaged therewith. The quick release coupling further includes a coupling adapter having a fluid passage therethrough and securable to the male member adjacent the body portion to establish fluid communication between the fluid passage and the fluid conduit, the coupling adapter being adapted to engage the second fluid line and including an adapter port adapted to establish fluid communication between the second fluid line and the fluid passage.

According to a possible embodiment, the handle portion comprises an outer surface, and wherein the restraining mechanism is provided along the outer surface of the handle portion.

According to one possible embodiment, the restraining mechanism comprises a groove extending circumferentially around the shank portion, the groove being shaped and adapted to receive a ball bearing assembly for preventing axial movement of the male member.

According to one possible embodiment, the groove extends circumferentially around the shank portion in a single plane.

According to one possible embodiment, the groove extends partially around the shank portion such that the groove includes a first end and a second end spaced apart from each other and defining a groove-free portion therebetween.

According to one possible embodiment, the non-grooved portion is shaped and adapted to engage a ball bearing assembly between a pair of adjacent bearing balls to prevent rotational movement of the male member.

According to one possible embodiment, the limiting mechanism further comprises a pawl adapted to engage the ball bearing assembly to prevent rotational movement of the male component.

According to one possible embodiment, the pawl comprises a plurality of recesses arranged along the groove for receiving respective bearing balls of the ball bearing assembly to prevent the rotational movement of the male part.

According to one possible embodiment, the detent includes a protrusion extending from the shank portion, the protrusion being shaped and dimensioned to engage the ball bearing assembly between a pair of adjacent bearing balls to prevent the rotational movement of the male component.

According to a possible embodiment, the protrusion extends from within the recess.

According to a possible embodiment, the protrusion is integrally formed with or welded to the handle portion.

According to a possible embodiment, the quick release coupling further comprises a valve assembly operable to control fluid flow along the fluid conduit of the male component before, during and after engaging the shank portion with the first fluid conduit.

According to a possible embodiment, the valve assembly comprises a valve head disposed within the fluid conduit proximate the handle portion port and operable in a closed position in which fluid flow is prevented through the handle portion port and an open position, the valve assembly further comprising a head spring connected to the valve head and adapted to bias the valve head in the closed position.

According to one possible embodiment, the valve assembly comprises a valve body disposed within the fluid conduit along the body portion and operable in a closed position blocking fluid flow through the fluid conduit and an open position allowing fluid flow through the fluid conduit, the valve assembly further comprising a body spring connected to the valve body and adapted to bias the valve body in the closed position.

According to one possible embodiment, the coupling adapter further comprises a housing having an inner surface comprising at least one radial surface and at least one axial surface, the inner surface defining a cavity having an open end, wherein the body portion of the male component is shaped and dimensioned to engage the cavity via the open end and abut the at least one radial surface.

According to one possible embodiment, the quick release coupling further comprises a nut securable within the cavity of the housing and surrounding a portion of the shank portion to radially constrain the male member, the nut being adapted to axially constrain the body portion within the cavity and allow the male member to rotate about the longitudinal axis of the shank portion relative to the housing and the nut so as to enable rotatable interconnection of the first and second fluid lines.

According to a possible embodiment, the quick release coupling further comprises a thrust washer surrounding the shank portion between the nut and the body portion.

According to a possible embodiment, the shank portion comprises a flange extending radially outwards and having a flange surface substantially perpendicular to the outer surface of the shank portion and facing the nut, and wherein the quick release coupling further comprises an outer sealing element surrounding the shank portion and extending between the flange surface and the nut.

According to another aspect, there is provided a male component for a quick release coupling connected with a hydraulic line provided with a female component comprising a ball bearing assembly, the male component having a fluid conduit therethrough, and the male component comprising: a handle portion extending along a longitudinal axis and adapted to engage the hydraulic line, the handle portion having a handle portion port adapted to establish fluid communication between the hydraulic line and the fluid conduit. The shank portion includes a limiting mechanism adapted to engage the ball bearing assembly to prevent rotation of the male member about the longitudinal axis.

According to a possible embodiment, the limiting mechanism comprises a groove extending circumferentially around the shank portion, the groove being shaped and adapted to receive the ball bearing assembly for preventing axial movement of the male member along the longitudinal axis.

According to one possible embodiment, the limiting mechanism further comprises a pawl adapted to engage the ball bearing assembly to prevent the rotational movement of the male component.

According to one possible embodiment, the pawl includes a plurality of grooves disposed along the grooves for receiving respective bearing balls of the ball bearing assembly to inhibit rotational movement of the male member.

According to another aspect, a quick release coupling for providing a connection between a pair of hydraulic lines is provided. The quick release coupling includes a male member having a fluid conduit therethrough and includes: a handle portion adapted to engage a first hydraulic line, the handle portion having a first port adapted to establish fluid communication between the first hydraulic line and the fluid conduit, the handle portion including a limiting mechanism adapted to cooperatively engage the first hydraulic line and to inhibit rotational and axial movement of the male component relative to the first hydraulic line when engaged therewith. The quick release coupling also has a coupling adapter connectable to the male member and having a fluid passage therethrough adapted for fluid communication with the fluid conduit, the coupling adapter being adapted to engage a second hydraulic line and including a second port adapted to establish fluid communication between the second hydraulic line and the fluid passage.

According to another aspect, there is provided the use of a quick release coupling for providing a connection between a pair of hydraulic lines. The quick release coupling includes a male member having a fluid conduit therethrough and includes: a handle portion adapted to engage a first hydraulic line, the handle portion having a first port adapted to establish fluid communication between the first hydraulic line and the fluid conduit, the handle portion including a limiting mechanism adapted to cooperatively engage the first hydraulic line and to inhibit rotational and axial movement of the male component relative to the first hydraulic line when engaged therewith. The quick release coupling further includes a coupling adapter connectable to the male member and having a fluid passage therethrough adapted for fluid communication with the fluid conduit, the coupling adapter being adapted to engage a second hydraulic line and including a second port adapted to establish fluid communication between the second hydraulic line and the fluid passage.

According to a possible embodiment, the quick release coupling is adapted to operate between about 0psi and 5000 psi.

According to a further aspect there is provided the use of a quick release coupling as defined above for providing a connection between a pair of hydraulic lines.

According to another aspect, a method of connecting a first fluid line to a second fluid line using a quick release coupling as described above is provided. The method comprises the following steps: connecting the coupling adapter to the second fluid line; and engaging the shank portion with the first fluid line to prevent rotational and axial movement of the quick release coupling relative to the first fluid line.

According to another aspect, a method of connecting a first fluid line provided with a female part to a second fluid line is provided. The method includes connecting a first end of a hydraulic coupling to the second fluid line; and connecting a second end of the hydraulic coupling to the first fluid line, the second end being provided with a male component configured to engage the female component and inhibit rotational and axial movement of the male component relative to the female component.

According to a possible embodiment, the hydraulic coupling is a quick release coupling.

Drawings

Fig. 1 is a perspective view of a quick lock release coupling according to a possible embodiment, which quick lock release coupling is provided with a restraining mechanism for preventing movement of a portion of the quick lock release coupling.

FIG. 2 is a side view of the quick lock release coupling shown in FIG. 1 showing male members and coupling adapters extending at opposite ends of the quick lock release coupling, according to one embodiment.

FIG. 3 is a front view of the quick lock release coupling of FIG. 1 showing a valve head disposed within a port of the coupling, according to one embodiment.

FIG. 4 is a cross-sectional view of the quick lock release coupling shown in FIG. 3 taken along line 4-4, showing a fluid conduit extending through the housing of the quick lock release coupling, according to one embodiment.

Fig. 5 to 8 are top views of various embodiments of the male component, showing possible embodiments of the limiting mechanism.

Fig. 9 is a perspective view of a quick lock release coupling according to another embodiment.

FIG. 10 is a side view of the quick lock release coupling of FIG. 9 showing male members and coupling adapters extending at opposite ends of the quick lock release coupling, according to one embodiment.

FIG. 11 is a front view of the quick lock release coupling of FIG. 9 showing a valve head disposed within a port of the coupling, according to one embodiment.

FIG. 12 is a cross-sectional view of the quick lock release coupling shown in FIG. 11 taken along line 12-12 showing a pressure relief disposed within the valve body, according to one embodiment.

Fig. 13 is a perspective view of a rotational coupling according to another embodiment.

FIG. 14 is a side view of the rotational coupling shown in FIG. 13, showing the male component coupled within the coupling adapter by a nut, according to one embodiment.

FIG. 15 is a front view of the rotational coupling shown in FIG. 13, showing a valve head disposed within a port of a male member, according to one embodiment.

FIG. 16 is a cross-sectional view of the rotational coupling shown in FIG. 15 taken along line 16-16 showing a flange portion of the male member disposed between the coupling adapter housing and the inner surface of the nut in accordance with one embodiment.

Fig. 17 is a perspective view of a rotational coupling according to another embodiment.

FIG. 18 is a side view of the rotational coupling shown in FIG. 17, showing a male component coupled within a coupling adapter by a nut, according to one embodiment.

FIG. 19 is a front view of the rotational coupling shown in FIG. 17, illustrating male component ports according to one embodiment.

FIG. 20 is a cross-sectional view of the rotational coupling shown in FIG. 19 taken along line 20-20 showing the shank portion of the male component coupled to a flange portion disposed within the coupling adapter housing in accordance with one embodiment.

FIG. 20A is an enlarged view of a portion of the rotational coupling shown in FIG. 20, illustrating a pair of seal rings disposed about the shank portion between the shank portion and the nut in accordance with one embodiment.

Fig. 21 is a perspective view of a rotational coupling according to another embodiment.

FIG. 22 is a cross-sectional view of the rotational coupling shown in FIG. 21, illustrating a shank portion defining a female coupling, in accordance with one embodiment.

Fig. 23 to 25 are top views of a coupling showing a coupling barrel (fig. 23), a swivel coupling (fig. 24) and a quick release Yang Lianzhou (fig. 25) according to a possible embodiment.

FIG. 25B is a perspective view of a multi-port swivel assembly provided with various embodiments of a coupling, according to one embodiment.

Fig. 25C is a cross-sectional view of another embodiment of a coupling showing a threaded connection port.

FIG. 26 is a top view of a pair of rotational couplings coupled to a multiport rotating assembly according to one embodiment.

Fig. 27 is a perspective view of a coupling provided with crimp fittings according to another embodiment.

Fig. 28 is a side view of the coupling shown in fig. 27, showing the coupling and extended crimp fitting fitted at opposite ends of the coupling according to one embodiment.

Fig. 29 is a front view of the coupling shown in fig. 27 according to one embodiment.

FIG. 30 is a cross-sectional view of the quick lock release coupling shown in FIG. 29 taken along line 30-30 illustrating a fluid conduit extending through the housing of the quick lock release coupling in accordance with one embodiment.

Figures 31 and 32 are representations of possible applications including one or more couplings showing a fishing boat pump (figure 31) prior to submersion and a fishing boat pump (figure 32) for operation under water.

FIG. 33 is an illustration of a hydraulic machine including a coupling mounted in a vertical configuration according to one possible embodiment.

Fig. 34 and 35 are perspective views of another embodiment of a coupling showing a catch element (fig. 35) having an elongated shape and extending partially circumferentially within a port of a male component (fig. 34).

Detailed Description

As will be explained below in connection with various embodiments, the present disclosure describes devices and systems for providing improved connection for hydraulic machines, such as quick lock release couplings configured to be coupled to and between hydraulic lines. The present disclosure describes a quick lock release coupling that can be easily and reliably connected to a hydraulic line adapted to deliver hydraulic fluid at an elevated pressure. The quick lock release coupling may include a male member shaped and dimensioned to engage a female member of a hydraulic line. The male component includes a limiting mechanism adapted to prevent movement of the male component relative to the hydraulic line (e.g., relative to the female component) when the male component is coupled to the hydraulic line. The female component conventionally includes a ball bearing assembly adapted to prevent axial movement of the male component while enabling rotation of the male component when the male component is coupled thereto. The limiting mechanisms described herein may be further adapted to prevent rotational movement of the male component. For example, the restraining mechanism may include a detent shaped and dimensioned to extend between a pair of adjacent balls of the ball bearing assembly, thereby preventing rotation of the male component.

It may thus be noted that the male part is adapted to remain substantially stationary with respect to the hydraulic line due to the restriction mechanism. Further, it will be appreciated that preventing movement of the male component relative to the hydraulic line may improve the life and efficiency of the various seal components of the quick lock release coupling due to the static assembly of the male component being subjected to less stress, less friction, less compressive forces, etc.

The quick lock release coupling may be configured to transport hydraulic fluid for various operations. The coupling may be implemented on a variety of equipment, machines and devices, such as forestry combine, industrial mowers, small track loader attachments, agricultural attachments, and the like. As will be described herein, the hydraulic coupling may be adapted to provide an interconnection between two fluid lines. The coupling enables coaxial interconnection of two fluid lines, but it will be appreciated that the coupling may be adapted to provide different interconnections, such as a 90 deg. connection or an angled connection. Alternatively or additionally, the quick lock release coupling may comprise an integrated swivel assembly adapted to move one or more hydraulic lines connected to the quick lock release coupling and provide a durable sealing capability prior to servicing.

Referring to fig. 1-4, an exemplary quick release coupling 10 (or simply "coupling") for interconnecting and establishing fluid communication between a pair of fluid lines is shown. The coupling 10 includes one or more components connected to each other and defining a central conduit 12 through the coupling 10. Thus, a fluid, such as hydraulic fluid, may flow through the coupling 10 via the central conduit 12. In some embodiments, the coupling 10 includes a first component configured to engage a first fluid line and a second component configured to engage a second fluid line, thereby connecting the fluid lines to one another. The first and second components are fixed to each other and each component defines a portion of the central conduit 12. In this embodiment, the central conduit 12 is generally longitudinal, with the inlet of the first component being substantially aligned with the inlet of the second component. However, it will be appreciated that other configurations are possible, such as having a curved or bent central tube 12.

In this embodiment, the first component of the coupling 10 may include a male component 14, the male component 14 defining a fluid conduit 15 therethrough and having a body portion 16 and a shank portion 18 extending from a first side of the body portion 16. As shown in fig. 4, the male component 14 has an inner surface 20 extending along the body portion 16 and the shank portion 18, the inner surface 20 defining the fluid conduit 15. In addition, as will be described further below, the stem portion 18 is adapted to engage a first fluid line and includes a first port or male member port 22 configured to establish fluid communication between the first fluid line and the fluid conduit 15.

In this embodiment, the second component of the coupling 10 includes a coupling adapter 24 defining a fluid passage 25 therethrough. The coupling adapter 24 is securable to the male component 14 in such a way that the fluid channel 25 communicates with the fluid conduit 15. Note that in this embodiment, the combination of the fluid conduit 15 and the fluid passage 25 forms the central conduit 12 of the coupling 10, although other configurations are possible. In this embodiment, the coupler adapter 24 is adapted to be secured to the body portion 16 of the male member 14 opposite the shank portion 18. For example, the body portion 18 and the coupler adapter 24 may have complementary shaped threads such that the coupler adapter 24 can be threaded into the body portion 18. In some embodiments, the coupling 10 includes an adapter seal 28 disposed between the coupling adapter 24 and the male component 14 to further secure the components together and prevent fluid leakage therebetween. As shown in fig. 2 and 4, the coupling adapter 24 is provided with an adapter port 26, which adapter port 26 is adapted to engage the second fluid line and establish fluid communication between the second fluid line and the fluid channel 25. It should therefore be noted that the first fluid line and the second fluid line are fluidly connected via the coupling 10, wherein the fluid flows through the fluid channel 25 and the fluid conduit 15 in either direction.

Still referring to fig. 1-4, the coupling 10 may be provided with a valve assembly 30, the valve assembly 30 being configured to control fluid flow through the coupling 10 (e.g., through the male member 14, through the coupling adapter 24, or a combination thereof). The valve assembly 30 is operable between a closed configuration in which fluid flow through the first port 22 is prevented and an open configuration in which fluid flow through the first port 22 is permitted. In this embodiment, the valve assembly 30 includes a valve head 32 disposed along the fluid conduit 15, more specifically, the valve head 32 is disposed within the first port 22. The valve head 32 is adapted to move between a closed position (see fig. 4) in which the valve head 32 blocks the first port 22, and an open position in which the valve head 32 is displaced such that the first port 22 becomes unblocked.

In this embodiment, the valve assembly 30 includes a resilient element 34, the resilient element 34 being coupled to the valve head 32 and configured to bias the valve head 32 in the closed position. For example, the resilient element 34 may include a spring 35, the spring 35 being operatively connected to the valve head 32 to bias the valve head 32 in the closed position. As shown in fig. 4, the spring 35 may extend along the fluid conduit 15 and abut an inner surface of the coupling adapter 24. Note that opening the valve assembly 30 (i.e., moving the valve head 32 to the open position) includes further moving the valve head 32 within the fluid conduit 15 (i.e., toward the coupler adapter 24), thereby compressing the spring 35 and opening the first port 22. In some embodiments, the female component may be provided with an actuator, such as a lever, configured to urge the valve head 32 when the handle portion 18 is engaged with the first fluid line. In other words, when pressed against the stem of the female member, the valve head collapses within the male member, thereby opening the first port 22. The valve head 32 illustratively has a flat outer surface 36, the outer surface 36 being adapted to be substantially coplanar with the end of the handle portion 18 when in the closed position.

In some embodiments, the stem portion 18 includes a limiting mechanism 40, the limiting mechanism 40 being adapted to prevent unwanted or accidental disengagement of the male component 14 from the first fluid line. For example, the restriction mechanism 40 may be disposed along an outer surface of the shank portion 18 for engaging an inner surface of the first fluid line. Conventionally, the first fluid line may comprise a female part (not shown) provided with a ball bearing assembly mounted circumferentially along the inner surface. Further, as shown in fig. 1,2 and 4, the restraining mechanism 40 includes a groove 42 extending circumferentially around the shank portion 18, the groove 42 being shaped and dimensioned to receive the ball bearing assembly therein. In this way, once the shank portion 18 engages the first fluid line, the ball bearing assembly and the groove 42 cooperate to resist axial movement of the male member 14 relative to the first fluid line, thereby preventing disengagement therefrom.

In some embodiments, the limiting mechanism 40 is further adapted to block rotational movement of the male component 14 relative to the first fluid line. More specifically, it should be noted that the ball bearing assembly is capable of rotating the male component 14 about its longitudinal axis (a). However, the limiting mechanism 40 may include a detent 44 shaped and sized to engage the ball bearing assembly to prevent rotation of the male component 14. The pawl 44 may be fixedly connected to the shank portion 18 such that engagement of the pawl 44 with the ball bearing assembly prevents rotation of the shank portion 18 (and thus the male member 14) about the longitudinal axis in either direction. As shown in fig. 2, the pawl 44 may include a protrusion 46 extending from the shank portion 18, the protrusion 46 being shaped and dimensioned to extend between a pair of adjacent ball bearings to inhibit rotation of the male member relative to the first fluid line.

In this embodiment, the projection 46 extends from within the recess 42 to facilitate engagement thereof with the ball bearing assembly (e.g., between a pair of adjacent ball bearings). Further, the projection 46 may be integrally formed as part of the shank portion 18 (e.g., during machining of the recess 42), although it will be appreciated that other configurations are possible. For example, referring to fig. 5-8, the detents 44 may be disposed about the shank portion 18 between the body portion 16 and the recess 42 (see fig. 5 and 6), or within the recess 42 (see fig. 7 and 8). In the embodiment of fig. 5, the pawl 44 may include a ball 48 or dome-shaped element connected to the shank portion 18 and extending from the shank portion 18 to engage a female component of the first fluid line. It should be noted that the female component may require additional complementarily shaped elements configured to engage the balls 48 to prevent rotational movement of the male component. The balls 48 may be spot welded to the shank portion 18, integrally formed with the shank portion 18, or attached to the shank portion 18 using any suitable method.

Alternatively, referring to fig. 6, the pawl 44 may include a tab 50 disposed along the outer surface of the shank portion 18 between the body portion 16 and the recess 42. In a similar manner to the balls 48, the protrusions 50 are configured to engage complementarily shaped elements of the female component for preventing rotation of the male component. In some embodiments, the complementarily shaped elements include recesses (not shown) having a shape conforming to the shape of the protrusions 50 such that the male component 14 is adapted to engage the female component in a predetermined orientation. It is to be appreciated that the male component 14 can include a plurality of detents 44 disposed about the shank portion 18 in the groove 42 and/or adjacent the groove 42.

In another embodiment, as shown in fig. 7, the pawl 44 may include one or more recesses 52 disposed about the shank portion 18 and/or within the groove 42. The recess 52 is shaped and sized to receive a ball bearing of the ball bearing assembly to prevent rotation of the male component 14 about the longitudinal axis. Note that the ball bearing assembly includes a limited number of ball bearings, and the pawl 44 may include any suitable number of recesses 52, such as fewer than the number of ball bearings, more than the number of ball bearings, or the same number. For example, the ball bearing assembly may include twelve (12) ball bearings, and the pawl 44 may include twenty-four (24) recesses 52 to facilitate engagement of the ball bearings with the pawl.

Referring now more particularly to fig. 8, in this embodiment, the pawl 44 includes a projection 46 disposed along the recess 42 and further includes a ball 48, the ball 48 being connected to the projection 46 and extending from the projection 46. The protrusions 46 may be adapted to prevent rotation of the male component 14 when the male component 14 is engaged with the female component, while the balls 48 may facilitate positioning the male component 14 with a pair of adjacent ball bearings on either side of the protrusions 46. It should be noted that the detents 44 of the limiting mechanism 40 may include any suitable component, feature, or combination thereof to prevent rotation of the male component 14. For example, in addition to having a protrusion 50 extending from the body portion 18 and between a pair of adjacent ball bearings, the pawl 44 may include a recess 52 disposed along the groove 42. It will be appreciated that any other combination of brakes 44 may be used and that any other combination of brakes 44 is possible.

Referring now to fig. 9-12, another embodiment of the coupling 10 will be described. The stem portion 18 and associated components (e.g., the limiting mechanism 40) may be substantially identical to the previous embodiments and adapted to engage the first fluid line and prevent axial and rotational movement of the male component. In this embodiment, the body portion 16 is elongated and includes an inner surface adapted to define one or more internal cavities 60 along the fluid conduit 15. Referring more particularly to fig. 12, the internal cavity 60 may include a first cavity 62 proximate the shank portion 18 and a second cavity 64 proximate the coupling adapter 24 when the coupling adapter 24 is connected to the male member 14.

In this embodiment, the valve assembly 30 further includes a valve body 70, the valve body 70 being mounted along the fluid conduit 15, for example, within the second cavity 64, and adapted to inhibit fluid flow between the first cavity 62 and the second cavity 64. The valve body 70 is adapted to move between a closed position, in which the valve body 70 blocks the fluid conduit 15 between the first cavity 62 and the second cavity 64, and an open position, in which the valve body 70 is moved, thereby allowing fluid flow. As shown in fig. 12, the inner surface of the body portion 16 may include an abutment surface 17, the abutment surface 17 being shaped and dimensioned such that the valve body 70 abuts against the abutment surface for preventing fluid flow through the fluid conduit 15. The valve assembly 30 may also include a second resilient element 72, such as a second spring 73, configured to bias the valve body 70 in the closed position (e.g., bias the valve body 70 against the abutment surface 17).

Further, the valve assembly 30 may include a valve body actuator 71 configured to move the valve body 70 from the closed position to the open position, thereby compressing the second spring 73 and enabling fluid flow. In this embodiment, the valve body actuator 71 includes a shaft 74 connected to the valve head 32 within the fluid conduit 15 and extending from the valve head 32. It is therefore noted that engaging the male component with the female component of the first fluid line causes the valve head 32 to retract within the fluid conduit 15, and subsequently causes the shaft 74 to engage the valve body 70 and urge the valve body 70 to move it to the open position. Thus, due to the distance between the stub shaft 77 and the valve body 70, the handle portion 18 may at least partially engage the female component before fluid communication is established between the first fluid line and the second fluid line.

In some embodiments, it may be desirable to at least partially control the pressure within the coupling 10, such as the fluid passage 25 and the fluid conduit 15 (e.g., within the first cavity 62 and/or the second cavity 64), to prevent failure or damage caused by pressure differential or pressurization issues. For example, hydraulic fluid may be provided to the second cavity 64 via a second fluid line, wherein the valve body 70 prevents fluid flow into the first cavity 62. Thus, it should be noted that the pressure within the second cavity 64 increases while the pressure within the first cavity 62 remains low (e.g., zero), making it difficult to move the valve body 70 to the open position to provide hydraulic fluid to the first fluid line. As such, in some embodiments, the valve body 70 may include a pressure eliminator 76, the pressure eliminator 76 being operable to eliminate or at least reduce the pressure within the first and second cavities 62, 64 prior to the valve body 70 moving to the open position.

In this embodiment, still referring to fig. 12, the valve body 70 has an aperture 75 defined therethrough, the aperture 75 communicating at a first end thereof with the first cavity 62 and at a second end thereof with the second cavity 64. A pressure relief 76 may be coupled to the valve body 70 within the bore 75 and operable to selectively relieve pressure within the second cavity to facilitate opening the valve body 70 (e.g., moving to an open position). More specifically, pressure eliminator 76 may include a blocking member, such as a plug 78, disposed within bore 75 and shaped and configured to block fluid flow therethrough. The plug 78 may be moved to enable a restricted flow of fluid from the second cavity 64 to the first cavity 62, thereby reducing (e.g., eliminating) the pressure within the second cavity 64, or at least creating a pressure balance between the first cavity and the second cavity (e.g., substantially the same pressure in each cavity). Thus, movement of the valve body 70 into the second cavity 64 is facilitated to operate it in the open position.

In some embodiments, the bore 75 may include a seat 80, the seat 80 being adapted to have the plug 78 positioned thereon when blocking fluid flow through the bore 75. As shown in fig. 12, in this embodiment, a seat 80 is disposed near the first end of the bore 75 (i.e., proximate the first cavity 62), and a plug 78 engages the seat 80 to prevent fluid flow through the bore 75. It should be noted that the plug 78 is movable between a seated position in which the plug 78 engages the seat 80 to block fluid flow and an unseated position in which the plug 78 is displaced from the seat 80 and spaced apart from the seat 80, thereby enabling fluid flow between the first and second cavities 62, 64. In this embodiment, the pressure eliminator 76 further includes a plug biasing element 82, the plug biasing element 82 being operatively connected to the plug 78 and configured to bias the plug 78 in the seated position. As will be described further below, the pressure relief 76 may be operated to exert a force on the plug 78 to displace and unseat it. Once the force is removed, the plug biasing element 82 is configured to return the plug 78 in the seated position, again preventing fluid flow through the bore 75.

In this embodiment, the pressure relief 76 further includes a cap 84, the cap 84 being shaped and sized to fit within the bore 75 to at least partially restrict fluid flow through the bore 75. In this embodiment, cap 84 is attached to valve body 70 within bore 75 by an interference fit, although other attachment methods are possible, such as by fasteners, by keying, by adhesives, and the like. A cap 84 is illustratively disposed adjacent the second end of the bore 75 so as to be located on the side of the second cavity 64. As shown in fig. 12, the plug biasing element 82 is connected to the cap 84 and extends between the cap 84 and the plug 78. In addition, the cap 84 includes a cap passage 85 defined therethrough for enabling fluid to flow from the second cavity 64 into the bore 75. Thus, when fluid is introduced into the second cavity 64 (e.g., via the second fluid line), fluid may flow into the bore 75 via the cap channel 85, although the plug 78 blocks fluid flow into the first cavity 62 when in the seated position.

As previously described, engaging the coupling 10 with the female component of the first fluid line causes the valve head 32 to retract within the fluid conduit 15, and subsequently causes the stub shaft 77 to engage the valve body 70 and push the valve body 70. Further, the plug 78 may have a portion that extends into the first cavity 62 when in the seated position. For example, in the embodiment shown in fig. 12, the plug 78 includes a generally spherical body 79 configured to engage the seat 80 in such a manner that a portion of the spherical body 79 communicates with the first cavity 62. In this way, moving the shaft 74 toward the valve body 70 causes the stub shaft 77 to engage the plug 78 within the bore 75 (e.g., toward the second cavity 64) and push the plug 78 inwardly prior to engaging the valve body 70. It should be noted, therefore, that a restricted flow rate of fluid is enabled between the first cavity 62 and the second cavity 64 through the aperture 75 as the plug 78 unseats via the stub shaft 77. It is also noted that flowing fluid between the chambers 62,64 causes a pressure drop in the second cavity 64, thereby facilitating movement of the valve body 70 into the second cavity 64 and into the open position, thereby establishing a greater flow rate of fluid into the first cavity and, thus, between the first and second fluid lines.

It should be appreciated that the coupling 10 includes a seal 90 or sealing element disposed between the various components for preventing fluid flow through the coupling 10 when fluid flow is not desired (e.g., when the coupling 10 is connected to only one of the first and second fluid lines). For example, the coupling 10 may include a shank portion seal 91, the shank portion seal 91 being disposed adjacent the male member port 22 such that the shank portion seal 91 engages the valve head 32 prior to engaging the coupling 10 with the first fluid line, as shown in fig. 12. Further, the coupling 10 may include an inner seal 92 disposed about the valve body 70 such that when the valve body 70 is in the closed position, the inner seal 92 engages the abutment surface 17 to prevent fluid flow through the gap between the valve body 70 and the body portion 16. It will be appreciated that the coupling 10 may include any suitable number of seals disposed between any of its adjoining components.

The above-described embodiments of the coupling provide a quick connect coupling or cartridge thereof (see fig. 17) that is configured to connect to complementary portions (e.g., male and/or female portions) and define a static connection therebetween. In particular, the coupling 10 is adapted to prevent axial movement between the male and female parts, for example by engagement of ball bearings of the female part with grooves of the male part. Further, the limiting mechanism 40 is configured to prevent rotational movement of the male and female components relative to each other. Thus, it will be appreciated that the coupling is adapted to resist axial and rotational movement between the male and female parts, thereby defining a static connection therebetween. It should be noted that providing a static connection may increase the life of the coupling by reducing stress, friction, etc. applied to various components of the coupling during operation.

Referring now to fig. 13-16, another implementation of a coupling is shown. In this embodiment, the coupling may be a rotational coupling 100, wherein the male component 14 is rotatably coupled to the coupling adapter 24 such that the first fluid line may rotate relative to the second fluid line. In other words, the coupling 100 provides a rotational connection between the first and second fluid lines. In this embodiment, the male component 14 includes a flange portion 102, which flange portion 102 extends radially outwardly from the body portion 16 at an end thereof opposite the shank portion 18. Furthermore, in this embodiment, the coupling adapter 24 includes a housing 104 defining an adapter cavity 105, the adapter cavity 105 being shaped to receive the body portion 16 of the male component 14 therein. As will be described further below, the rotational coupling 100 further includes a nut 110 insertable within the housing 105 for at least partially securing the male component 14 therein.

In some embodiments, the adapter cavity 105 includes an inner surface that includes at least one radial surface 106 and at least one axial surface 108. It should be understood that as used herein, the expression "radial surface" may refer to a surface that extends in a substantially perpendicular plane relative to the longitudinal axis (a) of the coupling 100. Similarly, it should be understood that as used herein, the expression "axial surface" may refer to a surface that is generally parallel to the longitudinal axis (a), and thus perpendicular relative to a radial surface. The inner surfaces 106,108 define an adapter cavity 105 having an open end 107 through which the male component 14 may be inserted. However, it will be appreciated that other configurations are possible, for example, the housing 104 may include a plurality of cavities into which a corresponding number of male components and nuts may be introduced. The inner surfaces 106,108 are preferably integrally formed with one another. This is typically produced by machining the housing 104 from a solid piece. Further, the housing 104 includes an outer surface 112 having any suitable finish and/or shape. For example, the outer surface 112 may have a generally cylindrical or circular shape. In the embodiment shown in fig. 13-16, the outer surface 112 is curved and is adapted to be retained within a retaining ring (not shown) mounted on the hydraulic machine and is capable of rotational freedom relative to the retaining ring.

In some embodiments, inserting the body portion 16 into the open end 107 of the adapter cavity 105 includes cooperatively abutting the flange portion 102 against an inner surface of the adapter cavity 105. Still referring to fig. 16, it will be appreciated that engaging the male component 14 within the housing 104 may establish fluid communication between the fluid conduit 15 of the male component 14 and the fluid passage 25 of the coupling adapter 24. In this embodiment, the fluid conduit 15 and the fluid channel 25 are substantially collinear, although it will be appreciated that other configurations may be used. For example, the fluid conduit 15 and the fluid channel 25 may have various orientations, depending on the desired application, such as a 90 ° angle or bevel.

In this embodiment, the flange portion 102 is integrally formed with the body portion 16 and extends from the body portion 16 such that the male component 14 has a generally T-shape. The flange portion 102 may be radially continuous and symmetrical, and may be disk-shaped and extend perpendicularly relative to the body portion 16. As will be described below, this configuration of the male component 14 may provide a support surface for resting against the inner surfaces of the housing 104 and nut 110, thereby distributing the forces (i.e., reducing pressure) exerted on the components of the coupling 100. However, it is understood that the flange portion 102 and/or any other component of the male component 14 may have any suitable shape that mates with the interior surface of the housing 104. In some embodiments, the flange portion 102 may include a score (not shown) defined on an outer circumferential surface thereof for enabling fluid flow between the flange portion 102 and the housing 104. This is useful for lubrication purposes and to define a self-lubricating coupling, such as described in applicant's U.S. patent No.8.047.579, which is incorporated herein by reference.

Referring still to fig. 13-16, a nut 110 may be secured within the adapter cavity 105 of the housing 104 and around the male component 14 to radially confine it within the adapter cavity 105. In some embodiments, the nut 110 may be adapted to surround the male component 14 from the port 22 to the flange portion 102, which allows for improved support, stability, and resistance to forces. In this embodiment, the nut 110 is secured around the body portion 16 of the male component 14 with the stem portion 18 and the port 22 extending beyond the nut 110 to facilitate connection with the first fluid line. In this embodiment, the nut 110 includes a projection 114 extending axially and internally into the cavity 105 of the housing 104 for axially restraining the flange portion 102 while allowing the male member 14 to rotate relative to the housing 104 and the nut 110. The male component 14 rotates about the longitudinal axis (a) of the shank portion 18.

In some embodiments, the nut 110 may have external threads and the inner surface of the housing 104 (i.e., the surface of the adapter cavity 105) may have corresponding internal threads to secure the nut 110 within the cavity of the housing. Alternatively, the components may be unthreaded and may be bolted, clamped, or otherwise connected to one another. As shown in fig. 13-16, the nut 110 includes a lip 116 extending over the peripheral edge 109 of the open end of the adapter cavity 105 to further secure the nut 110 into engagement with the coupler adapter 24.

In some embodiments, hydraulic pressure within the adapter cavity 105 pushes the male component 14 axially toward the nut 110. Once pressurized, the pressure within the housing 104 is substantially uniform in all directions and pushes vertically on the surface (e.g., against the flange portion 102 and the radial and axial surfaces 106, 108). In operation, fluid contained in the fluid conduit 15 and/or the fluid channel 25 is under hydraulic pressure. The operating pressure varies depending on the application, whether heavy or light. For example, typical ranges for hydraulic pressures in the forestry industry are between about 50 and about 4000psi, and in some cases up to about 5000psi. In a load sensing hydraulic circuit, the operating pressure varies most often between about 250psi and 3000 to 4000 psi.

In some embodiments, this pressure causes the flange portion 102 to directly abut against the ledge 114 of the nut 110. However, in this embodiment, the rotational coupling 100 further includes a slip ring 120 surrounding the body portion 16 and disposed between the nut 110 and the flange portion 102. Slip ring 120 may be adapted to reduce the coefficient of friction between the components, such as between flange portion 102 and nut 110, during rotation of male component 14. Slip ring 120 is particularly desirable in high pressure hydraulic systems (or in applications where fluid lubrication is less), because axial pressure on male component 14 greatly increases friction between flange portion 102 and nut 110. In some embodiments, slip ring 120 is formed from A material set, nyloilTM, nycastTM, teflon, or other suitable material composition for such a component. In some embodiments, the slip ring 120 may include a thrust washer adapted to support axial loads applied thereto, such as loads applied thereto by the flange portion 102 during operation and/or during hydraulic impact.

Referring to fig. 16, when the male component 14 is coupled within the adapter cavity 105, the flange portion 102 defines the axial play 95 with a radial surface 106 of the adapter cavity 105. More specifically, the internal depth of the adapter cavity 105 is greater than the sum of the width of the flange portion 102 and the length of the projection 114 of the nut 110, thereby enabling a certain amount of axial play 95. In some embodiments, the amount of axial play may be between about 0.005 inches and about 0.08 inches, although other configurations are possible, such as having a narrower axial play (e.g., <0.005 inches) or a wider axial play (e.g., >0.08 inches).

In this embodiment, when under internal fluid pressure, flange portion 102 is pushed toward projection 114 of nut 110, abutting slip ring 120. Slip ring 120 is adapted to achieve a force distribution, thereby reducing the pressure between the components. This in turn allows the rotational coupling 100 to have improved rotational performance at higher pressures (e.g., in the range of 3000 to 5000 psi). In some embodiments, the slip ring 120 has a flat disc shape, but may also have an O-ring shape to reduce the coefficient of friction. It should be noted that when the flange portion 102 is pressed against the slip ring 120, the flange portion 102 is maintained in a spaced relationship with the inner axial surface 108 of the adapter cavity 105 and corresponds to the amount of axial play 95. It should be noted that the axial play 95 defined within the adapter cavity 105 may help protect the various components of the coupling 100 from hydraulic shock (also referred to as a "hydraulic cylinder") or other types of fluid shock or pressure differential within and around the coupling.

In some embodiments, it may be desirable to maintain contact between flange portion 102, slip ring 120, and nut boss 114 to increase the sealing efficiency of coupling 100 (e.g., to prevent external fluids, dust, and/or debris from entering the coupling). During operation, hydraulic fluid flowing through the coupling 100 pushes the flange portion 102 against the slip ring 120, thereby creating contact between the flange portion 102, the slip ring 120, and the nut boss 114 and improving sealing efficiency. However, in some embodiments, the contact between these components may be broken, thereby compromising the sealing integrity of the coupling. 31-33, in an underwater application (FIGS. 31 and 32) without any pre-pressurization of the coupling, the vertical installation of the coupling, wherein the flange portion 102 tends to move away from the slip ring 120 under gravity (FIG. 33), or under hydraulic shock, and vacuum/suction effects occur within the coupling, may reduce the sealing integrity of the coupling, for example, by exerting pressure on the internal components of the coupling and breaking contact between the flange portion 102 and the slip ring 120. Under such conditions, the risk of dust, debris or other contaminants penetrating into the coupling increases and may cause problems.

Still referring to fig. 16, the rotational coupling 100 may include a seal assembly 130, the seal assembly 130 including at least one seal ring 132 (or O-ring), the seal ring 132 being adapted to mate with one or more of the male member 14, the nut 110, and the coupling adapter 24. In this embodiment, once the rotational coupling 100 is assembled and in operation, the seal assembly 130 is pressed between the male member 14 and the nut 110 to at least partially shut off the pressure of any fluid leaking through the gap of the coupling 100. The seal assembly 130 may be adapted to prevent fluid from leaking out of the coupling 100. In some embodiments, the seal assembly 130 may include an O-ring, a backup ring, or the like. Moreover, the seal assembly 130 may be easily replaced in the event that the seal assembly 130 loses its efficiency. The speed at which the fluid can be cut using the various sealing joints makes it less likely that if fluid leaks past one of the seals, it will leak past the next seal. In other words, a series of seals may be used as part of the seal assembly 130.

In some embodiments, the seal assembly 130 further includes one or more external seals 134 adapted to prevent fluid from leaking outside of the coupling 100 or to prevent debris and dust from entering the coupling 100. Referring to fig. 13-16, in this embodiment, the outer seal 134 includes a wiper ring 136 surrounding the male component 14 adjacent the shank portion 18. The wiper ring 136 is also adapted to engage the nut 110 to form a seal between the nut 110 and the male component 14. In some embodiments, the wiper ring 136 may have a flat disk shape, although other configurations are possible, as will be described below.

In this embodiment, the male component 14 includes an outer groove 140 extending around the shank portion 18. The outer groove 140 may be shaped and adapted to receive a portion of the wiper ring 136 therein. As shown in fig. 14 and 16, the wiper ring 136 may include an annular portion 138 adapted to engage the nut 110, and a protruding portion 139 extending from the annular portion 138 and engaging an outer groove 140. Note that both the annular portion 138 and the protruding portion 139 extend circumferentially around the male component 14, i.e., around the male component. In this embodiment, the outer groove 140 includes a groove wall 142, the groove wall 142 extending relatively perpendicularly with respect to the shank portion 18 so as to be substantially parallel to the front surface of the nut 110. Thus, the wiper ring 136 is shaped to extend between the nut 110 and the groove wall 142, the annular portion 138 engaging the nut 110 and the protruding portion 139 engaging the groove wall 142.

In some embodiments, wiper ring 136 is made of an elastic material, such as rubber, and is adapted to protect the various components of the coupling during operation of the hydraulic lines (e.g., when fluid flows between the first and second fluid lines via the coupling). During operation, it should be noted that the various components of the coupling 100 may be subjected to hydraulic shock (also referred to as "hydraulic cylinders"), which may cause movement, friction, damage, or failure of the components.

Some hydraulic shock may be caused by a pumping action resulting from a pressure differential between the fluid channel 25 and the fluid conduit. Specifically, hydraulic fluid may be provided to the fluid passage 25 via a second fluid line, wherein the valve body 70 prevents fluid from flowing into the fluid conduit 15. Thus, it should be noted that the pressure along the fluid channel 25 and within the adapter cavity 105 increases, while the pressure along the fluid conduit 15 remains low (e.g., zero). In this way, when the valve body 70 is displaced to the open position, a vacuum may be created by the low pressure within the fluid conduit, causing the pressure within the adapter cavity 105 to drop substantially rapidly to match the pressure along the fluid conduit 15 (e.g., 0 psi), thereby creating a pumping action within the coupling 100.

The pumping action (i.e., hydraulic impact) often generates a force against the flange portion 102 that pushes the flange portion 102 against the nut 110. In this embodiment, the nut 110 then pushes against a wiper ring 136 disposed about the male component. The resilient material of the wiper ring 136 is configured to deform to absorb at least some of the force generated by the hydraulic impact and reduce movement of the male component 14, the slip ring 120, and/or the nut 110. Once the pressure stabilizes and/or is released, i.e., once no more force is applied to the components of the coupling, the wiper ring 136 is adapted to return to its original shape and configuration, thereby also moving the nut 110 and/or male component 14 back into place.

As such, it will be appreciated that each time the coupling 100 is connected and/or disconnected from the first fluid line, the pressure within the adapter cavity 105 correspondingly increases and decreases, thereby creating a repetitive pumping action. The wiper ring 136 is configured to at least partially counteract this pumping action to protect the components of the coupling 100 (e.g., the male component 14) and the components connected thereto (e.g., the female component) to increase their life and efficiency.

In some embodiments, the wiper ring 136 may have a tapered shape, wherein the wiper ring has a diameter at a first end thereof that is greater than a diameter at an opposite second end thereof. For example, in this embodiment, the protruding portion 139 extends from the annular portion 138 at an angle such that the inner diameter of the wiper ring 136 along the annular portion 138 is greater than the inner diameter of the wiper ring along the protruding portion 139. Further, the thickness of wiper ring 136 along projection 139 is illustratively less than its thickness along annular portion 138. This configuration may increase the shock absorbing capacity of the wiper ring 136 and may also increase its resiliency (i.e., its ability to return to its original shape and configuration). During operation, hydraulic pressure within the coupling may cause wiper ring 136 to be compressed between nut 110 and groove wall 142, causing protrusions 139 to at least partially deform (e.g., bend) to absorb at least some of the force, for example, from a hydraulic cylinder. Once the pressure within the coupling stabilizes, the protruding portion 139 is adapted to return to its original configuration.

In some embodiments, the annular portion 138 and the protruding portion 139 may be made of the same material, thereby having substantially the same elasticity and/or flexibility. However, it should be understood that other configurations are possible. For example, the protruding portion 139 may be made of a more resilient or more flexible material than the annular portion 139. In such an embodiment, it should be noted that the annular portion 138 may absorb some of the force from the hydraulic impact, although the more resilient tab portion 139 is configured to absorb more force.

As shown in fig. 16, the second spring 72 illustratively extends between the inner surface of the adapter cavity 105 and the flange portion 102 and is adapted to absorb some of the force of the hydraulic shock and bias the flange portion 102 against the slip ring 120. Accordingly, the components of the coupling (e.g., flange portion 102, slip ring 120, and nut 110) are adapted to remain in contact with one another to ensure sealing efficiency of the coupling. The second spring 72 may be optional, with axial movement of the components of the coupling being at least partially blocked by the wiper ring 136 engaging the male component 14 (e.g., with the shank portion) and the nut 110. More specifically, under certain conditions, the flange portion 102 may move into the axial play 95, increasing the risk of collision with the housing and disconnection from the slip ring 120. In this embodiment, the groove wall 42 engages the wiper ring 136 when the male member 14 is urged toward the axial play 95 (e.g., by hydraulic shock, vertical installation, or under external pressure). The wiper ring 136 may be adapted to absorb some of the force and also engage the nut 110, which in turn, abuts the housing 104 via the lip 116. In this way, axial movement of the male part 14 towards the axial play 95 is blocked or at least reduced.

It should be noted that reducing or preventing movement of the components of the coupling (e.g., flange portion 102, slip ring 120, and nut 110) may reduce the stresses, deformations, and impacts they are subjected to during operation. Reducing the forces exerted on these components may increase their life, which reduces the need to replace and/or repair them, thereby increasing the efficiency and life of the coupling 100.

Referring broadly to fig. 1-16, it should be noted that when the male member 14 of the coupling (10 or 100) engages the female member of the first fluid line, the limiting mechanism 40 is adapted to prevent axial movement of the male member 14 relative to the female member (e.g., by engagement of a ball bearing assembly within a groove 42 provided about the shank portion 18). In addition, the limiting mechanism 40 is also adapted to prevent rotational movement of the male component 14 relative to the female component about the longitudinal axis of the handle portion 18 by engagement of the detents 44 with the ball bearing assembly.

Further, the flange portion 102 is shaped and sized to engage the adapter cavity 105, the nut 110 resists axial movement of the male component 14 toward the open end of the adapter cavity 105, and in some embodiments, the wiper ring 136 is adapted to resist or at least resist axial movement of the male component 14 toward the coupling adapter 24 (i.e., into the axial play 95). Thus, axial movement of the male component due to deformation and wear of the slip ring 120 (e.g., thrust washer) and suction and/or atmospheric pressure (e.g., when submerged in water) is also managed at least in part by the wiper ring 136 and maintains contact between the flange portion 102, the slip ring 120, and the nut boss 114. It should also be noted that since the wiper ring 136 is compressed into place between the groove wall 142 and the nut boss 114, the greater force exerted on the wiper ring 136 increases the sealing efficiency of the wiper ring 136, thereby further sealing the gap between the nut 110 and the male member 14. This may be desirable in certain situations, such as in vertical installations, or in underwater applications, where pressurization of the coupling prior to immersion is not required, as increased pressure from the water may increase the sealing efficiency of the wiper ring 136.

Referring now to fig. 17-20A, another embodiment of a coupling 100 is shown. The male component 14 is disposed within the housing 104 of the coupler adapter 24 with the shank portion 18 extending out of the housing 104 for connection with the female component. The coupling 100 further includes a nut 110 for connecting the male component 14 to the coupling adapter housing 104. Referring more particularly to fig. 20, the male component 14 may include a plurality of pieces coupled to one another. For example, in this embodiment, the male component 14 includes an inner part 180 and an inner shaft 184, the inner part 180 including a flange portion 102 disposed in the adapter cavity 105 proximate the coupling adapter 24, the inner shaft 184 extending from the flange portion 102 toward the open end 107. In addition, the male component 14 includes an outer part 182 that includes the shank portion 18. In this embodiment, the stem portion 18 is removably connected to the inner member 180 and extends out of the open end 107 of the adapter cavity 105. The handle portion 18 may include an outer shaft 186, the outer shaft 186 being shaped to couple with the inner shaft 184 to couple together the inner and outer parts of the male component 14.

In this embodiment, the inner and outer parts 180, 182 are coupled together by an interference fit between the inner and outer shafts 184, 186, although other coupling methods are possible, such as using fasteners, coupling by keying, coupling by adhesives, and the like. The inner part 180 is adapted to extend within the outer part 182 (i.e., the inner shaft 184 extends within the outer shaft 186). However, it will be appreciated that other configurations are possible, such as having the outer part 182 extend within the inner part 180 to connect the two parts to one another. In the illustrated embodiment, the outer shaft 186 is further adapted to engage the nut 110 such that the outer shaft 186 is connected between the inner shaft 184 and the nut boss 114, with the nut boss 114 coupled between the outer shaft 186 and the housing 104. Thus, it will be noted that the inner and outer parts 180, 182 of the male component 14 are secured to the housing by their cooperation with each other and with the nut 110.

Still referring to fig. 20, the handle portion 18 can include a cylinder 188 disposed between the outer shaft 186 and the port 22. The cylinder 188 is configured to engage the nut 110 to further connect the external part 182 (e.g., the shank portion 18) to the nut 110, and thus to the housing 104. The cylinder 188 generally has a larger diameter than the outer shaft 186 and the port 22. Thus, the nut 110 may have a shape complementary to the outer part 182 of the male component 14, e.g., the projection 114 of the nut 110 has an inner diameter adapted to receive the outer shaft 186, but prevents the cylinder 188 from being inserted therein. The nut 110 illustratively includes an outer end 111, the outer end 111 having a larger diameter than the projection 114 and being adapted to receive the cylinder 188 of the shank portion 18 therein.

In this embodiment, the outer end 111 defines a nut radial surface 113 adapted to face the cylinder 188. As will be described further below, the male member 14 is adapted to engage and mate with the nut 110 to define an axial clearance 95 between the flange portion 102 and the coupling adapter housing 104. Furthermore, the male component 14 engages the nut 110 in such a way that the cylinder 188 is spaced apart from the nut radial surface 113, defining a second axial play 195 therebetween. The axial play 95 and the second axial play 195 may generally have the same dimensions, although it is understood that, for example, one may be larger than the other.

In some embodiments, the seal assembly includes various seal elements, such as an O-ring disposed between the male component 14 and the nut 110, between the nut 110 and the housing 104, or a combination thereof. In this embodiment, referring to fig. 20 and 20A, the coupling 100 includes a plurality of seal rings 132, the seal rings 132 including a pair of seal rings 132 disposed within the outer end 111 of the nut 110 between the nut 110 and the cylindrical body 188 of the shank portion 18. The seal ring 132 is configured to seal a gap between the nut 110 and the male component 14 (e.g., the cylinder 188) and radially confine the male component 14 within the nut 110. Referring more particularly to fig. 20A, the seal ring 132 includes a first seal ring 132a and a second seal ring 132b disposed in a Zhou Xiangdai 189 defined about a cylinder 188. As described above, each seal ring 132 extends between and engages the nut 110 (on its inner surface) and the cylinder 188 (on its outer surface), radially constraining the cylinder 188 relative to the nut 110.

The first seal ring 132a engages a substantially planar surface such that it radially confines the male component 14 within the nut 110 and defines a seal therebetween. In this embodiment, the outer end 111 of the nut may have a tapered inner edge 115, with the second sealing ring 132b engaging the tapered inner edge 115. As such, the second seal ring 132b may be adapted to radially constrain the male component 14 (e.g., the outer part 182) and also at least partially provide axial constraint to the male component. For example, as described above, during operation, the coupling 100 may be subjected to a pumping action that may pull the male component 14 further into the adapter cavity 105, thereby pulling the cylinder 188 further into the outer end 111 of the nut 110. The tapered outer edge 115 may be shaped and configured to provide abutment for the second seal ring 132b, which second seal ring 132b may then inhibit axial movement of the cylinder 188 toward the nut 110. In other words, the second sealing ring 132b is adapted to be compressed between the side surface of the circumferential pocket 189 and the tapered inner edge 115, thereby preventing axial movement of the cylinder 188. It should be noted that by preventing axial movement of the cylinder 188, the outer part 182 does not push against the inner part 180, thereby maintaining the flange portion 102 in contact with the slip ring 120 within the adapter cavity 105. In some embodiments, the second seal ring 132b may be a pressure activated seal that at least partially blocks axial and radial movement of the male component and achieves higher sealing efficiency as pressure thereon increases.

It should be appreciated that adjusting the angle at which tapered inner edge 115 extends may correspondingly adjust the amount of axial restraint that second seal ring 132b may provide. For example, a tapered edge of about 45 degrees may be adapted to prevent axial movement over a greater pressure range than a tapered edge of about 10 degrees. In some embodiments, the tapered inner edge 115 of the nut 110 may be angled from about 5 degrees to about 85 degrees relative to the nut axial surface 117, although other configurations are possible. It should also be noted that the greater force exerted on the second seal ring 132b increases the sealing efficiency of the seal ring 132b because the cylinder 188 presses and squeezes the seal ring 132 between the outer ends of the nuts 111.

This may be desirable in certain situations, such as in a vertical installation (see fig. 33), or in an underwater application (see fig. 31 and 32), where the coupling need not be pressurized before being submerged, as the increased pressure from the water increases the sealing efficiency of the second sealing ring 132 b. For example, as shown in fig. 31 and 32, one or more couplings 100 may be connected to a subsea pump, such as a pump configured to collect fish as part of a commercial fishing vessel, prior to being submerged. The pump may then be submerged without pre-pressurizing the coupling to prevent water from penetrating the coupling. As shown in fig. 32, the pump may be lowered to about 20m below the surface before fluid is provided through the coupling, and the seal ring 132 (i.e., the second seal ring 132 b) is configured to prevent water and debris from entering the coupling 100. It will be appreciated that it is desirable to improve the sealing efficiency of the coupling when under water to prevent water from penetrating the coupling and mixing with hydraulic fluid, which may cause problems such as freezing fluid within the coupling, for example. It should be noted that the coupling connected to the pump may be a rotational coupling 100, or alternatively a non-rotational coupling, wherein one or more rotational couplings are mounted along the pump tubing, for example at regular intervals (e.g., every 10 m).

In some embodiments, the outer piece 182 of the male component 14 is removably connected to the inner piece 180 and within the nut 110. In this way, the outer part 182 may be disconnected from the inner part 180 so as to be interchangeable with another part. For example, the outer part 182 may be replaced with another male part outer part 182 (e.g., for maintenance or repair), or may be replaced with a corresponding female part. Referring to fig. 21 and 22, the coupling 100 may be adapted to define a female connection by replacing the male part's outer part 182 with a female part 190. The female component 190 is connected to the inner component 180 in a similar manner to the outer component 182 described above (e.g., the outer shaft 186 is coupled between the inner shaft 184 and the nut 110) and also engages the nut 110 via first and second seal rings 132a, 132b, the first and second seal rings 132a, 132b being configured to at least partially inhibit axial and radial movement of the female component relative to the nut 110 and the housing 104.

It should be noted that the coupling may comprise any of the mechanisms described above adapted to prevent or block some form of movement of the components of the coupling. In some embodiments, the coupling may include the restraining mechanism 40 and the outer seal 134 (e.g., the wiper ring 136 as shown in fig. 13, or the tapered inner edge 115 and the seal ring 132 as shown in fig. 20A), while in other embodiments, the coupling includes one of the restraining mechanism 40 and the outer seal 134, e.g., as shown in fig. 1 (i.e., only the restraining mechanism 40). It should also be noted that the coupling may be adapted to provide a connection between a pair of fluid lines, as described herein, although other configurations are possible. For example, the coupling may also interconnect more than two fluid lines, wherein the male component 14 may include a plurality of ports 22 and may be connected to a corresponding number of fluid lines. In some embodiments, a coupling may be coupled between the apparatus and the first hydraulic line, whereby the apparatus provides for the flow of hydraulic fluid.

23-25C, the quick release male coupling and related components (e.g., wiper ring 136 and/or tapered inner edge 115 and seal ring 132) and mechanisms (e.g., limiting mechanism 40) described herein may be included in various types of couplings suitable for various applications. For example, the limiting mechanism 40 may be provided on a coupling barrel 10a (fig. 23) adapted to be connected with a coupling housing, such as a rotary coupling housing (fig. 24), which is adapted for applications requiring manipulation of hydraulic lines in 3D space, such as in the forest industry. In other embodiments, the coupling may comprise a manifold type coupling, which may be a quick release Yang Lianzhou (fig. 25). Alternatively, referring to fig. 25B and 25C, the coupling may correspond to a rotary manifold coupling, which may include a quick lock (or quick release) capability 100B, a threaded connection 100C, a female connection 100d, and/or a threaded connection coupling 100e with a rotary joint. However, it will be appreciated that other configurations are possible and that the coupling may have any suitable size and/or shape. Further, as shown in fig. 26, the coupling may be part of a multi-port assembly 150, whereby multiple couplings, such as a rotational coupling 100, may be coupled to a locking plate 152, and the locking plate 152 may be connected to a hydraulic machine in any suitable manner.

Referring now to fig. 27-30, the coupling 10 may be provided with a crimp fitting 160 that may be connected to one end of the coupling 10 (e.g., to the male component 14). It should be noted that the crimp fitting or sleeve 160 is adapted to form a custom hydraulic hose assembly and defines a crimp end 162 of the coupling 10 (i.e., the end at which the crimp fitting 160 is provided), the crimp end 162 being adapted to be connected to a hydraulic line (e.g., a first fluid line). The crimp end 162 may be secured to the hydraulic line by a crimper or device, forming a permanent connection therebetween for repair or formation of the hydraulic line assembly. In this embodiment, the coupling may include a plurality of seal rings 132, the seal rings 132 including a seal ring 132c (e.g., an O-ring) between the crimp sleeve and the boss 114 of the nut 110 configured to prevent axial movement of the crimp sleeve 160 relative to the nut 110 and the housing 104, thereby preventing axial movement of the male component 14 in a similar manner.

It will be appreciated that in the embodiments described herein, the coupling may have improved sealing efficiency against external pressure, for example in underwater applications. Furthermore, when the seals around the couplings are pressed into place, the sealing efficiency of these couplings may increase with increasing ambient pressure, further sealing the gaps in the couplings. In some embodiments, the sealing element may provide axial and radial contact with one or more components of the coupling. These sealing elements may be adapted to at least partially block radial and axial movement of one or more components, thereby reducing stress exerted thereon and increasing the life thereof.

The present disclosure may be embodied in other specific forms. The described exemplary embodiments are to be considered in all respects only as illustrative and not restrictive. For example, it should be understood that the shape of the male component 14 may be varied in a variety of ways. Similarly, the internal shape of the adapter cavity 105 may be modified and should have a corresponding shape to accommodate the flange portion 102 and provide a support surface for distributing forces while allowing sufficient play for lubrication and movement. Further, the flange portion 102 may have an inclined or curved surface. These inclined or curved surfaces can affect fluid movement between the coupling surfaces and also affect force distribution. Since the pressurized fluid applies pressure perpendicularly relative to the solid surface of the coupling component, it will be appreciated that varying the angle and curvature and/or surface area of the male component may achieve different force distribution effects.

Furthermore, one or more of the components of one or more couplings and/or steps of the methods described herein may be modified, simplified, altered, omitted, and/or interchanged without departing from the scope of the present disclosure, depending on the particular application for which the coupling is intended and/or the desired end result, as briefly exemplified herein and as will also be apparent to those of skill in the art. For example, the limiting mechanism 40 may be modified to be able to interact and cooperate with components other than the ball bearing assembly. As shown in fig. 34 and 35, in some embodiments, the internal components of the female portion may include one or more locking elements 300, which locking elements 300 have an elongated shape and may extend at least partially circumferentially within the ports of the female portion, for example. As such, the male component may include a complementary shaped detent (e.g., recess 52) for receiving the latch element 300 therein. It should be noted that the catch elements 300 may be disposed at regular intervals around the male component 14 (e.g., around the shank portion 18), such as at 90 degree intervals, although other configurations are possible.

This disclosure is intended to cover and embrace all suitable changes in technology. The scope of the disclosure is, therefore, indicated by the appended claims rather than by the foregoing description. The scope of the claims should not be limited by the embodiments described in the examples, but should be given the broadest interpretation consistent with the description as a whole.

As used herein, the terms "coupled," "attached," "connected," or variants thereof may have several different meanings, depending on the context in which the terms are used. For example, the terms coupled, connected, or attached may have a mechanical connotation. For example, as used herein, the terms coupled, or attached may indicate that two elements or devices are connected to each other directly, or via one or more intermediate elements or devices, depending on the particular context.

In the above description, the same reference numerals denote similar elements. Moreover, for simplicity and clarity, i.e., so as not to unduly burden figures having several reference numbers, not all figures contain references to all of the components and features, and references to some of the components and features can be found in only one figure, and the components and features of the present disclosure shown in other figures can be readily inferred therefrom. The embodiments shown in the figures, the geometric configuration, the materials and/or dimensions mentioned are optional and are given for illustrative purposes only.

Furthermore, while the optional structures shown in the drawings include various components, and while the optional structures of the illustrated coupling may be comprised of certain geometries as explained and illustrated herein, not all of these components and geometries are required and therefore should not be taken in their limiting sense, i.e., should not be taken as limiting the scope of the present disclosure. It is to be understood that other suitable components and cooperation therebetween, as well as other suitable geometries, may be utilized and employed with the coupling and corresponding parts, as briefly described and as readily inferred therefrom, without departing from the scope of the present disclosure.

Claims

1. A quick release coupling for providing a connection between a first fluid line and a second fluid line, the first fluid line being provided with a female component comprising a ball bearing assembly, the quick release coupling comprising:

a male component having a fluid conduit therethrough, and comprising:

a body portion having an inner surface at least partially defining the fluid conduit; and

a handle portion extending from the body portion and adapted to engage the female portion of the first fluid line, the handle portion having a handle portion port adapted to establish fluid communication between the first fluid line and the fluid conduit, the handle portion including a limiting mechanism adapted to engage the ball bearing assembly and prevent rotational and axial movement of the male member relative to the first fluid line when the first fluid line is engaged; and

A coupler adapter having a fluid passage therethrough and securable to the male member adjacent the body portion to establish fluid communication between the fluid passage and the fluid conduit, the coupler adapter being adapted to engage the second fluid line and including an adapter port adapted to establish fluid communication between the second fluid line and the fluid passage.

2. The quick release coupling of claim 1, wherein the shank portion comprises an outer surface, and wherein the restraining mechanism is disposed along the outer surface of the shank portion.

3. A quick release coupling according to claim 1 or 2, wherein the restraining mechanism comprises a groove extending circumferentially around the shank portion, the groove being shaped and adapted to receive the ball bearing assembly for resisting the axial movement of the male component.

4. A quick release coupling according to claim 3, wherein the groove extends circumferentially around the shank portion in a single plane.

5. The quick release coupling of claim 3 or 4, wherein the groove extends partially around the shank portion such that the groove includes a first end and a second end spaced apart from one another and defining a groove-free portion therebetween.

6. The quick release coupling of claim 5, wherein said non-grooved portion is shaped and adapted to engage said ball bearing assembly between a pair of adjacent bearing balls to prevent said rotational movement of said male member.

7. The quick release coupling of any one of claims 1 to 4, wherein the restraining mechanism further comprises a pawl adapted to engage the ball bearing assembly to prevent the rotational movement of the male component.

8. The quick release coupling of claim 7, wherein the pawl includes a plurality of recesses disposed along the groove for receiving respective bearing balls of the ball bearing assembly to inhibit the rotational movement of the male member.

9. The quick release coupling of claim 7 or 8, wherein the pawl includes a protrusion extending from the shank portion, the protrusion being shaped and dimensioned to engage the ball bearing assembly between a pair of adjacent bearing balls to prevent the rotational movement of the male member.

10. The quick release coupling of claim 9, wherein the protrusion extends from within the recess.

11. A quick release coupling according to claim 9 or 10, wherein the protrusions are integrally formed with or welded to the shank portion.

12. The quick release coupling of any one of claims 1 to 11, further comprising a valve assembly operable to control fluid flow along the fluid conduit of the male component before, during and after engaging the shank portion with the first fluid conduit.

13. The quick release coupling of claim 12, wherein the valve assembly comprises a valve head disposed within the fluid conduit proximate the handle portion port and operable in a closed position in which fluid flow is prevented through the handle portion port and an open position, the valve assembly further comprising a head spring connected to the valve head and adapted to bias the valve head in the closed position.

14. The quick release coupling of claim 12 or 13, wherein the valve assembly comprises a valve body disposed within the fluid conduit along the body portion and operable in a closed position blocking fluid flow through the fluid conduit and an open position allowing fluid flow through the fluid conduit, the valve assembly further comprising a body spring connected to the valve body and adapted to bias the valve body in the closed position.

15. The quick release coupling of any one of claims 1 to 14, wherein the coupling adapter further comprises a housing having an inner surface comprising at least one radial surface and at least one axial surface, the inner surface defining a cavity having an open end, wherein the body portion of the male component is shaped and dimensioned to engage the cavity via the open end and abut the at least one radial surface.

16. The quick release coupling of claim 15, further comprising a nut securable within the cavity of the housing and surrounding a portion of the shank portion to radially constrain the male member, the nut adapted to axially constrain the body portion within the cavity and allow the male member to rotate about a longitudinal axis of the shank portion relative to the housing and the nut to rotatably interconnect the first and second fluid lines.

17. The quick release coupling of claim 16, further comprising a thrust washer surrounding the shank portion between the nut and the body portion.

18. The quick release coupling of claim 16 or 17, wherein the shank portion includes a flange extending radially outward and having a flange surface substantially perpendicular to the outer surface of the shank portion and facing the nut, and wherein the quick release coupling further comprises an outer sealing element surrounding the shank portion and extending between the flange surface and the nut.

19. A male component for a quick release coupling connected to a hydraulic line, the hydraulic line being provided with a female component comprising a ball bearing assembly, the male component having a fluid conduit therethrough, and the male component comprising:

a handle portion extending along a longitudinal axis and adapted to engage the hydraulic line, the handle portion having a handle portion port adapted to establish fluid communication between the hydraulic line and the fluid conduit,

the stem portion includes a limiting mechanism adapted to engage the ball bearing assembly to prevent rotation of the male component about the longitudinal axis.

20. The male component of claim 19, wherein the shank portion comprises an outer surface, and wherein the restraining mechanism is disposed along the outer surface of the shank portion.

21. A male component according to claim 19 or claim 20, wherein the restraining means comprises a groove extending circumferentially around the shank portion, the groove being shaped and adapted to receive the ball bearing assembly for resisting axial movement of the male component along the longitudinal axis.

22. The male component of any of claims 19 to 21, wherein the limiting mechanism further comprises a detent adapted to engage the ball bearing assembly to prevent the rotational movement of the male component.

23. The male component of claim 22, wherein the pawl comprises a plurality of recesses disposed along the groove for receiving respective bearing balls of the ball bearing assembly to prevent the rotational movement of the male component.

24. The male component of claim 22 or 23, wherein the detent comprises a protrusion extending from the shank portion, the protrusion being shaped and dimensioned to engage the ball bearing assembly between a pair of adjacent bearing balls to prevent the rotational movement of the male component.

25. The male component of claim 24, wherein the protrusion extends from within the recess.

26. The male component of claim 24 or 25 wherein the protrusion is integrally formed with or welded to the shank portion.

27. A quick release coupling for providing a connection between a pair of hydraulic lines, comprising:

a male component having a fluid conduit therethrough, and comprising:

a handle portion adapted to engage a first hydraulic line, the handle portion having a first port adapted to establish fluid communication between the first hydraulic line and the fluid conduit, the handle portion including a limiting mechanism adapted to cooperatively engage the first hydraulic line and to inhibit rotational and axial movement of the male component relative to the first hydraulic line when engaged therewith; and

a coupler adapter connectable to the male member and having a fluid passage therethrough adapted for fluid communication with the fluid conduit, the coupler adapter being adapted to engage a second hydraulic line and including a second port adapted to establish fluid communication between the second hydraulic line and the fluid passage.

28. Use of a quick release coupling for providing a connection between a pair of hydraulic lines, the quick release coupling comprising:

a male component having a fluid conduit therethrough, and comprising:

29. Use of a quick release coupling according to claim 28, wherein the quick release coupling is adapted to operate between about 0psi and 5000 psi.

30. Use of a quick release coupling according to any of claims 28 or 29, characterized in that the quick release coupling comprises the features of any of claims 1 to 18.

31. Use of a quick release coupling according to any one of claims 1 to 26 for providing a connection between a pair of hydraulic lines.

32. A method of connecting a first fluid line to a second fluid line using a quick release coupling according to any one of claims 1 to 26, the method comprising:

connecting the coupling adapter to the second fluid line; and

the handle portion is engaged with the first fluid line to prevent rotational and axial movement of the quick release coupling relative to the first fluid line.

33. The method of claim 32, wherein the quick release coupling is adapted to operate between approximately 0psi and 5000 psi.

34. A method of connecting a first fluid line provided with a female part to a second fluid line, comprising:

connecting a first end of a hydraulic coupling to the second fluid line; and

Connecting a second end of the hydraulic coupling to the first fluid line, the second end being provided with a male component configured to engage the female component and prevent rotational and axial movement of the male component relative to the female component.

35. The method of claim 34, wherein the hydraulic coupling is a quick release coupling.

36. The method of claim 35, wherein the quick release coupling comprises any of the features of any of claims 1 to 18.