CA1242226A - Flow check mechanism - Google Patents
Flow check mechanismInfo
- Publication number
- CA1242226A CA1242226A CA000452053A CA452053A CA1242226A CA 1242226 A CA1242226 A CA 1242226A CA 000452053 A CA000452053 A CA 000452053A CA 452053 A CA452053 A CA 452053A CA 1242226 A CA1242226 A CA 1242226A
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- Canada
- Prior art keywords
- ball
- spring
- force
- cylindrical bore
- recess
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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- Quick-Acting Or Multi-Walled Pipe Joints (AREA)
- Check Valves (AREA)
Abstract
A FLOW CHECK MECHANISM
Abstract of the Disclosure A flow check mechanism is disclosed which is useful in a female coupler for preventing closure of a male coupler coupled thereto should a vacuum occur in the female coupler. The flow check mechanism includes a housing having a cylindrical bore formed therein with an inlet port at one end and an outlet port at an opposite end. Formed within the cylindrical bore, between the inlet and outlet ports, is a pair of recesses. A resilient ball is positioned in the cylindrical bore between the pair of recesses and has an outside diameter slightly larger than the inside diameter of cylindrical bore but less than the diameter of either of the recesses. The flow check mechanism further includes first and second springs positioned in the cylindrical bore between the inlet port and the ball and between the ball and the outlet port, respectively. The springs retain the ball in contact with the inner periphery of the cylindrical bore when the fluid pressure forces acting on opposite sides of the ball are approximately equal. When the fluid pressure impinging on a given side of the resilient ball exceeds the fluid and spring forces on the opposite side of the ball, the ball will move into alignment with the respective recess and relieve the fluid pressure forces acting thereon. Since springs of different spring forces may be used, it is possible for the resilient ball to permit fluid flow in one direction at a low pressure and to permit fluid flow in the opposite direction at a higher pressure.
Abstract of the Disclosure A flow check mechanism is disclosed which is useful in a female coupler for preventing closure of a male coupler coupled thereto should a vacuum occur in the female coupler. The flow check mechanism includes a housing having a cylindrical bore formed therein with an inlet port at one end and an outlet port at an opposite end. Formed within the cylindrical bore, between the inlet and outlet ports, is a pair of recesses. A resilient ball is positioned in the cylindrical bore between the pair of recesses and has an outside diameter slightly larger than the inside diameter of cylindrical bore but less than the diameter of either of the recesses. The flow check mechanism further includes first and second springs positioned in the cylindrical bore between the inlet port and the ball and between the ball and the outlet port, respectively. The springs retain the ball in contact with the inner periphery of the cylindrical bore when the fluid pressure forces acting on opposite sides of the ball are approximately equal. When the fluid pressure impinging on a given side of the resilient ball exceeds the fluid and spring forces on the opposite side of the ball, the ball will move into alignment with the respective recess and relieve the fluid pressure forces acting thereon. Since springs of different spring forces may be used, it is possible for the resilient ball to permit fluid flow in one direction at a low pressure and to permit fluid flow in the opposite direction at a higher pressure.
Description
A FLOW CHECK M~CH~NISM
Field of the Invention This invention relates to a flow check mechanism and more particularly to a flow check mechanism Eor a iemale coupler.
Background Of The Invention Numerous female couplers are currently available for coupling to and uncoupling from a pressurized or non-pressurized male coupler. Such couplers are used extensively in hydraulic hook-ups which are used extensively on a~ricultural and industrial vehicles. One problem with using such couplers in pairs is that there is a tendency for a vacuum to occur within one oE the female couplers under certain situations which causes the male coupler on the return side of the circuit to close thereby blocking ~luid flow. One solution to the problem was described in Canadian application number 439,336 filed 19 October 1983 by Kugler et àl and assigned to the assignee o~
this application. A disadvantage of this earlier flow check mechanism is that it is rather complicated in construction and costly to manufacture.
Now an inexpensive flow check mechanism has been invented which will prevent the male check valve on the return side of a hydraulic circui-t Erom closing should a vacuum occur in the adjacent female coupler or should a high return flow force occur on the male check valve.
Summary of the Invention Briefly, this invention relates to a flow check mechanism which is especially useful in a female coupler. The ~low check mechanism includes a housing having a cylindrical bore formed therein with an inlet port at one end and outlet port in the opposite end. Located between the two ports is a recess formed about the inner periphery of the dylindrical bore. A resilient ball is positioned in the cylindrical bore adjacent to the recess. The resilient ball has an outside diameter slightly larger than the inside diameter of the bore and less than the diameter of the recess. The ball is retained in position by first and second springs which are positioned in the bore between the inlet port and the ball and between the ball and the outle-t port, respectively. The springs assist in urging the ball back to a set position once the ball has been displaced by pressurized ~luid. The ball is moveable rightward into 1 alignment with the recess to relieve pressure acting on its left surface when this left side pressure, plus the force of the second spring, is greater than the fluid pressure acting on the right side of the ball plus the force from the first spring.
The general object of this invention is to provide a flow check mechanism. A more specific object of this invention is to provide a flow check mechanism which can be used in a female coupler to prevent closure of an engaged male coupler should a vacuum occur in the female coupler or should a high return flow force occur on the male check valveO
Another object of this invention is to provide a relatively simple and economical flow check mechanism.
Still further, an object of this invention is to provide a flow check mechanism which checks flow in one direction at a low pressure and relieves fluid in an opposite direction at a higher pressure.
Other objects and advaotages of the present invention will become more apparent to those skilled in the art and view oE the following description and the accompanying drawings.
~rief Description of the Drawings Fig. 1 is a cross-sectional view of a female coupler having a flow check mechanism.
Fig. 2 is a partial cross-sectional view of Fig. 1 showing the position of the flow check mechanism when the female coupler is coupled to a male coupler.
Fig. 3 is a partial cross-sectional view of Fi~. 1 showing the pOSitiQn of the flow check mechanism when there is fluid pressure in the piston cavity.
Fig. 4 is a partial cross-sectional view of Fig. 1 showing the flow check mechanism when bleeding occurs from the piston cavity during the coupling and uncoupling process.
Fig. 5 is a partial cross-sectional view of Fig. 1 showing the position of the flow check mechanism when relieving thermally e~panded fluid from the piston cavity.
Detailed Description of the Preferred Embodiment Referring to Fig. 1, a female coupler 10 is shown which is designed to receive a male coupler (not shown). For purposes of convenience and not by way of limitation, the viewers right will be taken as the right-hand side of the female coupler 10~ The female coupler 10 includes a housing 12 haviny a bore 14 formed 1 therein, which preferably is open at each end. Movably positioned within the bore 14 is a receptacle 16 which contains a main cavity 18 and a passageway 20. The passageway 20 opens into an engagement bore 22 into which a male coupler is insertableO Preferablyr the main cavity 18 is centrally located within the receptacle 16 while the engagement bore 22 is located at the right end thereof. Fluid can be directed into the main cavity 18 through a first port 24 and out of the main cavity 18 through a second port 26. The first port 24 comm~nicates with a conduit 28 which has a directional control valve 30 positioned thereacross. The directional control valve 30 regulates the flow of pressuri2ed fluid into, and so~etimes out of the main cavity 18. As indicated in Fig. 1, the first port 24 can be either a single port or a plurality of ports formed in the periphery of the receptacle 16. While the first port 24 will permit fluid flowing in either~direction, the second port 26 is primarily an o~tlet port which permits fluid flow out of the main cavity 18 and into a reservoir (not shown). The fluid which enters the reservoir could then be rec~ycled and used again 20 within the hydraulic circuit.
Positioned within the main cavity 18 is a moveable main valve 32, which is preferably a poppet valve. Formed on the ri~ht-hand end of the main valve 32 is a ste~ 34 which projects through the passageway 20 and into the engagement port 22 when the main valve 32 is in a closed position, as shown. Positioned ~ust to the left of the stem 34 and formed in the periphery of the main valve 32 is a beveled surface 36. The beveled surface 36 mates with an interior valve seat 38 formed adjacent to the left peripheral surface of the passageway 20. When the beveled surface 36 is seated against the interior valve seat 38, the passageway 20 is blocked. In the blocked position, the main valve 32 is in its rightmost position as shown. The ~ain valve 32 also includes an internal passage 40 which provides fluid communication between the first port 24 and the second port 26.
35 A pair of recesses 42 and 44 are formed on the inner periphery of the internal passage 40, and the purpose of these recesses will be explained shortly.
The second or outlet port 26 is preferably circular in cross section and is axially aligned with the elongated central axis 40 of the receptacle 16. The second port 26 is constructed in an ?P
1 end member 46 and has a tapered outer surface 4B which mates with a similarly tapered inner surface 50 formed on the receptacle 16. The end member ~6 is held secure to the receptacle 16 by a snap ring 52. The second port 26 is formed having two diEferent internal diameters, 54 and 56, which are interconnected by a conical surface 58. The smaller of the two internal diameters 56 is located in the left or outer portion of the end member 46.
A secondary valve 60 is positioned in the second port 26 and is moveable between an open and a closed position. The secondary valve 60, which is preferably a poppet valve, also has a flat left-hand surEace 66 which projects out of the left-hand end of the female coupler 10 when the secondary valve 60 is in a closed position. The secondary valve 60 is opened by the contact of a lever-actuated cam 68 which is pivotally secured to the housing 12 by a pin 70~ The lever-actuated cam 68 includes first and second cam lobes 72 and 74 and a lever arm 76. For the sake of simplicity, the lever arm 76 will be described as initially being positioned in a horizonal plane where it is capable of being raised. By raising the lever arm 76 to a position indicated by the dotted line in Fig. 1, the first cam lobe 72 will be brought into contact with the left end of the receptacle 16. This action will urge the receptacle 16 to the right to facilitate engagement of a male coupler. As the lever arm 76 is raised further, the second cam lobe 74 will contact the left-hand surface 66 of the secondary valve 60 and cause it to move rightward to an open position. Preferably, the secondary valve 60 will open just prior to the time that the male coupler is fully received within the engagement bore 22.
The opening of the secondary valve 60 also provides an outlet for any fluid which may be trapped in the main cavity 18.
Positioned within the main cavity 18, between the first and second ports 24 and 26, is a moveable piston 78. The piston 78 has a sleeve-like conEiguration which is in slidable contact with both the outer periphery of the main valve 3~ and with the .. - .
3 ~r ~ ~_ ~ ~ k~
1 inside surface of the receptacle 16. The piston 78 has a left-hand end surface 80 and a right-hand end surface 82. Positioned on the inner circumference of the piston 7~ is a shoulder 84 which is contacted by a left end surface 86 of the main valve 32 as the main valve 32 is moved leftwards. A spring 87 is positioned between the left-hand surface 80 and the end member 46 and is designed to impart a force onto the piston 78 to constantly force it and the main valve 32 ric~htward. A more detailed description of the operation is stated below.
For purposes of convenience, the chamber between the piston 78 and the end member ~6 will be defined as a piston cavity 88.
As fluid flows into the piston cavity 88 it will impinge on the left-hand surface 80 of the piston 78 and cause the piston 78 to move rightward. The extent of the rightward movement of the piston 78 is limited by a shoulder 90 formed on the inner periphery of the receptacle 16~while the leftward movement of the piston 78 is limited by contact with the end member ~6.
A collar 92 is also positioned in the ~ain cavity 18 which encircles a portion of the main valve 32. The collar 92 has a right-hand end s~rface 94 and a left-hand end surface 96. The right-hand end surface ~4 is in constant contact with a compression spring 98 which encircles the right-hand portion of the main valve 32. The compression spring 98 abuts a retainer ring 9g which is positioned adjacent to an annular seal 100.
25 The retainer ring 99 and the seal 100 are preferably positioned adjacent to the base of the stem 34. The left-hand end surface 96 of the collar 92 abuts a retainer ring 102 which is positioned in a groove 104 formed on the inner circumference of the receptacle 18~ The combination of the compression spring 98 and the retainer ring 102 serve to limit the travel of the collar 92. In addition; the compression spring g8 urges the main valve 32 to the right so that the beveled surface 36 seats against the interior valve seat 38, ~s shown in Fig. 1. The compression spring 98 should have a sufficient spring force to 35 hold the main valve 32 in a closed position thereby blocking fluid flow through the passageway 20 when a male coupler is not inserted into the engagement bore 22.
As shown in Fig. 1, a vent 106 is provided in the receptacle 18 just to the left of the collar 92. This vent 106 provides an 40 escape for any fluid that may become trapped between the piston 1 78 and the collar 92. Preferably, the fluid which escapes through the vent 106 will be directed back to a reservoir such that it can be reused again.
The female coupler 10 i5 shown having a flow check mechanism 108 which is positioned in the internal passage 4~ of the main valve 32 between the first and second ports 24 and 26, respectively. The flow check mechanism 108 includes a resilient ball 110 positioned between the first and second recesses ~2 and 4~, respectively. The resilient ball 110, which is constructed of a synthetic material, for example neoprene, has an outside diameter slightly larger than the inside diameter of the internal passage 40 and less than the diameter of either of the recesses 42 or 44. The resilient ball 110 is retained between the recesses 42 and 44 by first and second springs 112 and 114, respectively. The first spring 112 is positioned in the internal passage 40 to the right of the resilient ball 110 and has a higher spring force than the second spring 114. The second spring 114 is positioned in the internal passage 40 to the left oP the resilient ball 110. The second spring 114 is very flexible in nature and therefore is guided b~ the elongated pin 64 and the inner perLphery of the internal passage 40.
Preferably, the second spring 114 has a very low spring force, preferably in the range of 1 to 6 pounds per inch.
Operation In Fig. 1 the resilient ball 110 is shown when the female coupler 10 is in an uncoupled position. In this position, the resilient ball 110 is positioned adjacent to the second recess 44 and is compressed slightly so as to form a tight seal with the inner periphery of the internal passage 40.
In normal operation, as a male coupler is inserted into the engagement bore 22, the main valve 32 will move leftward until its left-hand surface 86 abuts the shoulder 84 of the piston 78. Depending upon the amount of pressure exerted on the main valve 32 by the male coupler, the main valve 32 and the piston 35 78 will move leftward together towards the end member 46.
During this time, the secondar~ valve 60 is in an open position due to the contact with the lobe 74 of the the lever-actuated cam 68~ Maximum leftward movement of the main valve 32 and the piston 78 is shown in Fig. 4 wherein actual contact is made 40 between the left-hand surface 80 of the piston 78 and the right-~x~q~
1 hand surface of the end member 46~ At this time, the spring 87is compressed but as soon as the secondary valve 60 is closed, the spring 87 will force the piston 78 and the main valve 32 rightward such that the stem 34 will again be in contact with the ball of the male check member. It should be noticed that during this time the resilient ball 110 will move leftward under the influence of fluid pressure into alignment with the second recess 44 such that the fluid can flow around the resilient ball 110 and through the internal passage 40 from the main cavity 18 to the piston cavity 88. Once the male coupler is fully received in the engagement bore 22 the lever-actuated cam 68 will be returned to its initial position and the secondary valve 60 will close. At this point, pressurized fluid can be introduced through the conduit 28 by opening the directional control valve 30. The initial surge of fluid will be divided into two paths; one path will flow towards the passageway 20 to the male coupler while the second path will be through the internal passage 40 towards the piston cavity 88, see Fig. 2.
The surge of fluid will force the resilient ball 110 into alignment with the second recess 44 and provide a flow path around the resilient ball 110 into the piston cavity 88. As the pressure increases in the piston cavity 88, it will impinge on the right-hand surface 62 of the secondary valve 60 and assure that the secondary valve 60 remains closed. As the force of the incoming fluid equals the force of the fluid on the left side of the resilient ball 110, the force of the second spring 114 will reposition the resilient ball 110 such that it contacts the inner periphery of the first passage 40. This action will seal off fluid flow through the inner passage 40.
Since it is common to use a pair of female couplers 10 and a pair of male couplers in a closed loop hydraulic circuit, such as between an agricultural tractor and a hydraulic implement, it is normal for the operator to reverse the direction of fluid flow at various times so as to raise or lower an attached implement. As the operator reverses the direction of flow, so that the fluid will flow from one of the male couplers through an adjacent female coupler, there may be experienced a pressure drop in the main cavity 18. When this occurs, the pressure of the fluid in the piston cavity 88 plus the force of the second 40 spring 114 may be sufficient to cause the resilient ball 110 to g ~
1 move rightward. Such rightward movement will compress the first spring 112 as the resilient ball 110 approaches the first recess 42. If the pressure difference between the ~ain cavity 18 and the piston cavity 88 is sufficiently large to overcome the spring force of the first spring 112l the resilient ball 110 will roll into alignment with the first recess 42 and permit the higher pressurized fluid to flow rightward illtO the main cavity 18. ~ig. 3 shows such a situation just be~ore the resilient ball 110 rolls into alignment with the first recess 42~
Fig. 5 shows a situation where the resilient ball 110 is in alignment with the first recess 42 and the higher pressurized fluid present in the piston cavity 88 can be relieved from piston cavity 88 to the main cavity 18. Such a situation also occurs due to the thermal expansion of fluid within the piston cavity 88 when the female coupler 10 is either coupled to or uncoupled from a male coupler.~ By relieving the pressurized fluid from the piston cavity 88, one is assured that no damage will occur to the internal components o~ the female coupler 10.
It should be noted that when the resilient ball 110 is in alignment with the second recess 44, see Figs. 2 and 4, the first sprlng 112 will be ~ully extended and free from contact with the resilient ball 110. This means that the force needed to move the resilient ball 110 rightwards, back into the sealing arrangements with the inner periphery of the internal passage 40, will be slightly greater than the force of the pressurized fluid i~pinging on the right side of the resilient ball 110. It should also be noted that due to the difference in the spring forces, a higher force is required to move the resilient ball 110 into alignment with the first recess 42 than is needed to 30 move the ball 110 into alignment with the second recess 44.
This difference will mean that when the resilient ball 110 is positioned adjacent to the second recess 44, a flow check valve is obtained, while when the resilient ball 110 is in alignment with the first recess 42, a relief valve is obtained.
While the invention has been described in coniuction with a specific embodiedment, it is to be understood that man~
alternatives, modifications, and variations will be apparent to those skilled in the art in light of the aforegoing description. Accordingly, this invention is intended to embrace :
1 all such alternatives, modifications, and variations which fall within the spirit and scope of the appended claims.
~0 ~0 _ 9 _
Field of the Invention This invention relates to a flow check mechanism and more particularly to a flow check mechanism Eor a iemale coupler.
Background Of The Invention Numerous female couplers are currently available for coupling to and uncoupling from a pressurized or non-pressurized male coupler. Such couplers are used extensively in hydraulic hook-ups which are used extensively on a~ricultural and industrial vehicles. One problem with using such couplers in pairs is that there is a tendency for a vacuum to occur within one oE the female couplers under certain situations which causes the male coupler on the return side of the circuit to close thereby blocking ~luid flow. One solution to the problem was described in Canadian application number 439,336 filed 19 October 1983 by Kugler et àl and assigned to the assignee o~
this application. A disadvantage of this earlier flow check mechanism is that it is rather complicated in construction and costly to manufacture.
Now an inexpensive flow check mechanism has been invented which will prevent the male check valve on the return side of a hydraulic circui-t Erom closing should a vacuum occur in the adjacent female coupler or should a high return flow force occur on the male check valve.
Summary of the Invention Briefly, this invention relates to a flow check mechanism which is especially useful in a female coupler. The ~low check mechanism includes a housing having a cylindrical bore formed therein with an inlet port at one end and outlet port in the opposite end. Located between the two ports is a recess formed about the inner periphery of the dylindrical bore. A resilient ball is positioned in the cylindrical bore adjacent to the recess. The resilient ball has an outside diameter slightly larger than the inside diameter of the bore and less than the diameter of the recess. The ball is retained in position by first and second springs which are positioned in the bore between the inlet port and the ball and between the ball and the outle-t port, respectively. The springs assist in urging the ball back to a set position once the ball has been displaced by pressurized ~luid. The ball is moveable rightward into 1 alignment with the recess to relieve pressure acting on its left surface when this left side pressure, plus the force of the second spring, is greater than the fluid pressure acting on the right side of the ball plus the force from the first spring.
The general object of this invention is to provide a flow check mechanism. A more specific object of this invention is to provide a flow check mechanism which can be used in a female coupler to prevent closure of an engaged male coupler should a vacuum occur in the female coupler or should a high return flow force occur on the male check valveO
Another object of this invention is to provide a relatively simple and economical flow check mechanism.
Still further, an object of this invention is to provide a flow check mechanism which checks flow in one direction at a low pressure and relieves fluid in an opposite direction at a higher pressure.
Other objects and advaotages of the present invention will become more apparent to those skilled in the art and view oE the following description and the accompanying drawings.
~rief Description of the Drawings Fig. 1 is a cross-sectional view of a female coupler having a flow check mechanism.
Fig. 2 is a partial cross-sectional view of Fig. 1 showing the position of the flow check mechanism when the female coupler is coupled to a male coupler.
Fig. 3 is a partial cross-sectional view of Fi~. 1 showing the pOSitiQn of the flow check mechanism when there is fluid pressure in the piston cavity.
Fig. 4 is a partial cross-sectional view of Fig. 1 showing the flow check mechanism when bleeding occurs from the piston cavity during the coupling and uncoupling process.
Fig. 5 is a partial cross-sectional view of Fig. 1 showing the position of the flow check mechanism when relieving thermally e~panded fluid from the piston cavity.
Detailed Description of the Preferred Embodiment Referring to Fig. 1, a female coupler 10 is shown which is designed to receive a male coupler (not shown). For purposes of convenience and not by way of limitation, the viewers right will be taken as the right-hand side of the female coupler 10~ The female coupler 10 includes a housing 12 haviny a bore 14 formed 1 therein, which preferably is open at each end. Movably positioned within the bore 14 is a receptacle 16 which contains a main cavity 18 and a passageway 20. The passageway 20 opens into an engagement bore 22 into which a male coupler is insertableO Preferablyr the main cavity 18 is centrally located within the receptacle 16 while the engagement bore 22 is located at the right end thereof. Fluid can be directed into the main cavity 18 through a first port 24 and out of the main cavity 18 through a second port 26. The first port 24 comm~nicates with a conduit 28 which has a directional control valve 30 positioned thereacross. The directional control valve 30 regulates the flow of pressuri2ed fluid into, and so~etimes out of the main cavity 18. As indicated in Fig. 1, the first port 24 can be either a single port or a plurality of ports formed in the periphery of the receptacle 16. While the first port 24 will permit fluid flowing in either~direction, the second port 26 is primarily an o~tlet port which permits fluid flow out of the main cavity 18 and into a reservoir (not shown). The fluid which enters the reservoir could then be rec~ycled and used again 20 within the hydraulic circuit.
Positioned within the main cavity 18 is a moveable main valve 32, which is preferably a poppet valve. Formed on the ri~ht-hand end of the main valve 32 is a ste~ 34 which projects through the passageway 20 and into the engagement port 22 when the main valve 32 is in a closed position, as shown. Positioned ~ust to the left of the stem 34 and formed in the periphery of the main valve 32 is a beveled surface 36. The beveled surface 36 mates with an interior valve seat 38 formed adjacent to the left peripheral surface of the passageway 20. When the beveled surface 36 is seated against the interior valve seat 38, the passageway 20 is blocked. In the blocked position, the main valve 32 is in its rightmost position as shown. The ~ain valve 32 also includes an internal passage 40 which provides fluid communication between the first port 24 and the second port 26.
35 A pair of recesses 42 and 44 are formed on the inner periphery of the internal passage 40, and the purpose of these recesses will be explained shortly.
The second or outlet port 26 is preferably circular in cross section and is axially aligned with the elongated central axis 40 of the receptacle 16. The second port 26 is constructed in an ?P
1 end member 46 and has a tapered outer surface 4B which mates with a similarly tapered inner surface 50 formed on the receptacle 16. The end member ~6 is held secure to the receptacle 16 by a snap ring 52. The second port 26 is formed having two diEferent internal diameters, 54 and 56, which are interconnected by a conical surface 58. The smaller of the two internal diameters 56 is located in the left or outer portion of the end member 46.
A secondary valve 60 is positioned in the second port 26 and is moveable between an open and a closed position. The secondary valve 60, which is preferably a poppet valve, also has a flat left-hand surEace 66 which projects out of the left-hand end of the female coupler 10 when the secondary valve 60 is in a closed position. The secondary valve 60 is opened by the contact of a lever-actuated cam 68 which is pivotally secured to the housing 12 by a pin 70~ The lever-actuated cam 68 includes first and second cam lobes 72 and 74 and a lever arm 76. For the sake of simplicity, the lever arm 76 will be described as initially being positioned in a horizonal plane where it is capable of being raised. By raising the lever arm 76 to a position indicated by the dotted line in Fig. 1, the first cam lobe 72 will be brought into contact with the left end of the receptacle 16. This action will urge the receptacle 16 to the right to facilitate engagement of a male coupler. As the lever arm 76 is raised further, the second cam lobe 74 will contact the left-hand surface 66 of the secondary valve 60 and cause it to move rightward to an open position. Preferably, the secondary valve 60 will open just prior to the time that the male coupler is fully received within the engagement bore 22.
The opening of the secondary valve 60 also provides an outlet for any fluid which may be trapped in the main cavity 18.
Positioned within the main cavity 18, between the first and second ports 24 and 26, is a moveable piston 78. The piston 78 has a sleeve-like conEiguration which is in slidable contact with both the outer periphery of the main valve 3~ and with the .. - .
3 ~r ~ ~_ ~ ~ k~
1 inside surface of the receptacle 16. The piston 78 has a left-hand end surface 80 and a right-hand end surface 82. Positioned on the inner circumference of the piston 7~ is a shoulder 84 which is contacted by a left end surface 86 of the main valve 32 as the main valve 32 is moved leftwards. A spring 87 is positioned between the left-hand surface 80 and the end member 46 and is designed to impart a force onto the piston 78 to constantly force it and the main valve 32 ric~htward. A more detailed description of the operation is stated below.
For purposes of convenience, the chamber between the piston 78 and the end member ~6 will be defined as a piston cavity 88.
As fluid flows into the piston cavity 88 it will impinge on the left-hand surface 80 of the piston 78 and cause the piston 78 to move rightward. The extent of the rightward movement of the piston 78 is limited by a shoulder 90 formed on the inner periphery of the receptacle 16~while the leftward movement of the piston 78 is limited by contact with the end member ~6.
A collar 92 is also positioned in the ~ain cavity 18 which encircles a portion of the main valve 32. The collar 92 has a right-hand end s~rface 94 and a left-hand end surface 96. The right-hand end surface ~4 is in constant contact with a compression spring 98 which encircles the right-hand portion of the main valve 32. The compression spring 98 abuts a retainer ring 9g which is positioned adjacent to an annular seal 100.
25 The retainer ring 99 and the seal 100 are preferably positioned adjacent to the base of the stem 34. The left-hand end surface 96 of the collar 92 abuts a retainer ring 102 which is positioned in a groove 104 formed on the inner circumference of the receptacle 18~ The combination of the compression spring 98 and the retainer ring 102 serve to limit the travel of the collar 92. In addition; the compression spring g8 urges the main valve 32 to the right so that the beveled surface 36 seats against the interior valve seat 38, ~s shown in Fig. 1. The compression spring 98 should have a sufficient spring force to 35 hold the main valve 32 in a closed position thereby blocking fluid flow through the passageway 20 when a male coupler is not inserted into the engagement bore 22.
As shown in Fig. 1, a vent 106 is provided in the receptacle 18 just to the left of the collar 92. This vent 106 provides an 40 escape for any fluid that may become trapped between the piston 1 78 and the collar 92. Preferably, the fluid which escapes through the vent 106 will be directed back to a reservoir such that it can be reused again.
The female coupler 10 i5 shown having a flow check mechanism 108 which is positioned in the internal passage 4~ of the main valve 32 between the first and second ports 24 and 26, respectively. The flow check mechanism 108 includes a resilient ball 110 positioned between the first and second recesses ~2 and 4~, respectively. The resilient ball 110, which is constructed of a synthetic material, for example neoprene, has an outside diameter slightly larger than the inside diameter of the internal passage 40 and less than the diameter of either of the recesses 42 or 44. The resilient ball 110 is retained between the recesses 42 and 44 by first and second springs 112 and 114, respectively. The first spring 112 is positioned in the internal passage 40 to the right of the resilient ball 110 and has a higher spring force than the second spring 114. The second spring 114 is positioned in the internal passage 40 to the left oP the resilient ball 110. The second spring 114 is very flexible in nature and therefore is guided b~ the elongated pin 64 and the inner perLphery of the internal passage 40.
Preferably, the second spring 114 has a very low spring force, preferably in the range of 1 to 6 pounds per inch.
Operation In Fig. 1 the resilient ball 110 is shown when the female coupler 10 is in an uncoupled position. In this position, the resilient ball 110 is positioned adjacent to the second recess 44 and is compressed slightly so as to form a tight seal with the inner periphery of the internal passage 40.
In normal operation, as a male coupler is inserted into the engagement bore 22, the main valve 32 will move leftward until its left-hand surface 86 abuts the shoulder 84 of the piston 78. Depending upon the amount of pressure exerted on the main valve 32 by the male coupler, the main valve 32 and the piston 35 78 will move leftward together towards the end member 46.
During this time, the secondar~ valve 60 is in an open position due to the contact with the lobe 74 of the the lever-actuated cam 68~ Maximum leftward movement of the main valve 32 and the piston 78 is shown in Fig. 4 wherein actual contact is made 40 between the left-hand surface 80 of the piston 78 and the right-~x~q~
1 hand surface of the end member 46~ At this time, the spring 87is compressed but as soon as the secondary valve 60 is closed, the spring 87 will force the piston 78 and the main valve 32 rightward such that the stem 34 will again be in contact with the ball of the male check member. It should be noticed that during this time the resilient ball 110 will move leftward under the influence of fluid pressure into alignment with the second recess 44 such that the fluid can flow around the resilient ball 110 and through the internal passage 40 from the main cavity 18 to the piston cavity 88. Once the male coupler is fully received in the engagement bore 22 the lever-actuated cam 68 will be returned to its initial position and the secondary valve 60 will close. At this point, pressurized fluid can be introduced through the conduit 28 by opening the directional control valve 30. The initial surge of fluid will be divided into two paths; one path will flow towards the passageway 20 to the male coupler while the second path will be through the internal passage 40 towards the piston cavity 88, see Fig. 2.
The surge of fluid will force the resilient ball 110 into alignment with the second recess 44 and provide a flow path around the resilient ball 110 into the piston cavity 88. As the pressure increases in the piston cavity 88, it will impinge on the right-hand surface 62 of the secondary valve 60 and assure that the secondary valve 60 remains closed. As the force of the incoming fluid equals the force of the fluid on the left side of the resilient ball 110, the force of the second spring 114 will reposition the resilient ball 110 such that it contacts the inner periphery of the first passage 40. This action will seal off fluid flow through the inner passage 40.
Since it is common to use a pair of female couplers 10 and a pair of male couplers in a closed loop hydraulic circuit, such as between an agricultural tractor and a hydraulic implement, it is normal for the operator to reverse the direction of fluid flow at various times so as to raise or lower an attached implement. As the operator reverses the direction of flow, so that the fluid will flow from one of the male couplers through an adjacent female coupler, there may be experienced a pressure drop in the main cavity 18. When this occurs, the pressure of the fluid in the piston cavity 88 plus the force of the second 40 spring 114 may be sufficient to cause the resilient ball 110 to g ~
1 move rightward. Such rightward movement will compress the first spring 112 as the resilient ball 110 approaches the first recess 42. If the pressure difference between the ~ain cavity 18 and the piston cavity 88 is sufficiently large to overcome the spring force of the first spring 112l the resilient ball 110 will roll into alignment with the first recess 42 and permit the higher pressurized fluid to flow rightward illtO the main cavity 18. ~ig. 3 shows such a situation just be~ore the resilient ball 110 rolls into alignment with the first recess 42~
Fig. 5 shows a situation where the resilient ball 110 is in alignment with the first recess 42 and the higher pressurized fluid present in the piston cavity 88 can be relieved from piston cavity 88 to the main cavity 18. Such a situation also occurs due to the thermal expansion of fluid within the piston cavity 88 when the female coupler 10 is either coupled to or uncoupled from a male coupler.~ By relieving the pressurized fluid from the piston cavity 88, one is assured that no damage will occur to the internal components o~ the female coupler 10.
It should be noted that when the resilient ball 110 is in alignment with the second recess 44, see Figs. 2 and 4, the first sprlng 112 will be ~ully extended and free from contact with the resilient ball 110. This means that the force needed to move the resilient ball 110 rightwards, back into the sealing arrangements with the inner periphery of the internal passage 40, will be slightly greater than the force of the pressurized fluid i~pinging on the right side of the resilient ball 110. It should also be noted that due to the difference in the spring forces, a higher force is required to move the resilient ball 110 into alignment with the first recess 42 than is needed to 30 move the ball 110 into alignment with the second recess 44.
This difference will mean that when the resilient ball 110 is positioned adjacent to the second recess 44, a flow check valve is obtained, while when the resilient ball 110 is in alignment with the first recess 42, a relief valve is obtained.
While the invention has been described in coniuction with a specific embodiedment, it is to be understood that man~
alternatives, modifications, and variations will be apparent to those skilled in the art in light of the aforegoing description. Accordingly, this invention is intended to embrace :
1 all such alternatives, modifications, and variations which fall within the spirit and scope of the appended claims.
~0 ~0 _ 9 _
Claims (10)
IS CLAIMED ARE DEFINED AS FOLLOWS:
1. A flow check mechanism comprising:
a) a housing having a cylindrical bore formed therein with an inlet port at one end and an outlet port at an opposite end, said housing having a recess formed about the inner periphery of said cylindrical bore;
b) a resilient ball positioned in said cylindrical bore and having an outside diameter slightly larger than the inside diameter of said cylindrical bore and less than the diameter of said recess; and c) first and second springs positioned in said cylindrical bore between said inlet port and said ball and between said ball and said outlet port, respectively, said springs assisting in urging said ball back to a set position adjacent said recess once said ball has been displaced by fluid pressure, said ball being movable into alignment with said recess to relieve a fluid pressure force acting on said outlet port side of said ball when said fluid pressure force, plus the force of said second spring, is greater than a fluid pressure force acting on said inlet port side of said ball plus the force of said first spring.
a) a housing having a cylindrical bore formed therein with an inlet port at one end and an outlet port at an opposite end, said housing having a recess formed about the inner periphery of said cylindrical bore;
b) a resilient ball positioned in said cylindrical bore and having an outside diameter slightly larger than the inside diameter of said cylindrical bore and less than the diameter of said recess; and c) first and second springs positioned in said cylindrical bore between said inlet port and said ball and between said ball and said outlet port, respectively, said springs assisting in urging said ball back to a set position adjacent said recess once said ball has been displaced by fluid pressure, said ball being movable into alignment with said recess to relieve a fluid pressure force acting on said outlet port side of said ball when said fluid pressure force, plus the force of said second spring, is greater than a fluid pressure force acting on said inlet port side of said ball plus the force of said first spring.
2. The flow check mechanism of claim 1 wherein said first spring has a higher spring force than said second spring.
3. A flow check mechanism comprising:
a) a housing having a cylindrical bore formed therein with an inlet port at one end and outlet port at an opposite end, said housing having first and second spaced-apart recesses formed about the inner periphery of said cylindrical bore;
b) a resilient ball positioned in said cylindrical bore between said first and second recesses, said ball having an outside diameter slightly larger than the inside diameter of said cylindrical bore and less than the diameter of either of said recesses; and c) first and second springs positioned in said cylindrical bore between said inlet port and said ball and between said ball and said outlet port, respectively, said springs assisting in urging said ball back to a set position adjacent said second recess once said ball has been displaced by fluid pressure, said ball being movable rightward into alignment with said first recess to relieve a fluid pressure force acting on a left surface of said ball when a fluid pressure force acting on said left surface, plus the force of said second spring, are substantially greater than a fluid pressure force acting on a right surface of said ball plus the force of said first spring.
a) a housing having a cylindrical bore formed therein with an inlet port at one end and outlet port at an opposite end, said housing having first and second spaced-apart recesses formed about the inner periphery of said cylindrical bore;
b) a resilient ball positioned in said cylindrical bore between said first and second recesses, said ball having an outside diameter slightly larger than the inside diameter of said cylindrical bore and less than the diameter of either of said recesses; and c) first and second springs positioned in said cylindrical bore between said inlet port and said ball and between said ball and said outlet port, respectively, said springs assisting in urging said ball back to a set position adjacent said second recess once said ball has been displaced by fluid pressure, said ball being movable rightward into alignment with said first recess to relieve a fluid pressure force acting on a left surface of said ball when a fluid pressure force acting on said left surface, plus the force of said second spring, are substantially greater than a fluid pressure force acting on a right surface of said ball plus the force of said first spring.
4. The flow check mechanism of claim 3 wherein said first spring has a higher spring force than said second spring.
5. The flow check mechanism of claim 3 wherein said first spring is completely extended when said ball is moved leftward from an initial position between said first and second recesses toward said second recess such that once said ball is aligned with said second recess, the amount of force needed to move said ball back into a sealing arrangement with the inner periphery of said cylindrical bore is equal to a pressurized fluid force equal to the force of pressurized fluid impinging a right surface of said ball plus the force of said second spring.
6. A female coupler having a flow check mechanism for preventing closure of an attached male coupler should a vacuum occur in said female coupler when fluid flow from said male coupler to said female coupler is momentarily blocked by a directional control valve, said female coupler comprising:
a) a housing;
b) a receptacle movably positioned within said housing said receptacle having a main cavity formed therein which is joined by a passageway to an engagement bore located at one end of said receptacle and into which a male coupler is engageable, a valve seat formed about the periphery of one end of said passageway, and first and second ports communicating with said main cavity;
c) main valve means for controlling fluid flow through said passageway, said main valve means including a valve member having an internal passage formed therein which provides fluid communication between said first and second ports, a recess formed about the inner periphery of said internal passage, and a valve stem extending outward from said valve member which projects through said passageway and into said engagement bore when said main valve means is in a closed position;
d) secondary valve means for controlling fluid flow through said second port, said secondary valve means being movable between an open and a closed position;
e) lever-actuatable cam means for linearly moving said receptacle within said housing and for moving said secondary valve means from said closed to said open position;
f) piston means operable when coupling to a male coupler for assisting in moving said main valve means against excessive pressure contained in the attached male coupler, said piston means being positioned within said main cavity between said first and second ports and having a first surface against which fluid can impinge and a second surface which contacts a portion of said main valve means;
g) a stop positioned within said main cavity for limiting the movement of said main valve means towards said second port;
and h) flow check means for regulating fluid pressure acting on said first surface of said piston, said flow check means including a resilient ball positioned in said internal passage, said resilient ball having an outside diameter slightly larger than the inside diameter of said internal passage and less than the diameter of said recess, and first and second springs positioned in said internal passage between said first port and said ball and between said ball and said second port, respectively, said springs assisting in urging said ball back to a set position adjacent said recess once said ball has been displaced by fluid pressure, said ball being movable into alignment with said recess to relieve fluid pressure forces acting on said piston when fluid pressure acting on said second port side of said ball, plus the force of said second spring, is greater than fluid pressure acting on said first port side of said ball, plus the force of said first spring, thereby permitting said main valve means to move leftward assuring that an opening is established between said female coupler and said male coupler even when a vacuum is present in said main cavity.
a) a housing;
b) a receptacle movably positioned within said housing said receptacle having a main cavity formed therein which is joined by a passageway to an engagement bore located at one end of said receptacle and into which a male coupler is engageable, a valve seat formed about the periphery of one end of said passageway, and first and second ports communicating with said main cavity;
c) main valve means for controlling fluid flow through said passageway, said main valve means including a valve member having an internal passage formed therein which provides fluid communication between said first and second ports, a recess formed about the inner periphery of said internal passage, and a valve stem extending outward from said valve member which projects through said passageway and into said engagement bore when said main valve means is in a closed position;
d) secondary valve means for controlling fluid flow through said second port, said secondary valve means being movable between an open and a closed position;
e) lever-actuatable cam means for linearly moving said receptacle within said housing and for moving said secondary valve means from said closed to said open position;
f) piston means operable when coupling to a male coupler for assisting in moving said main valve means against excessive pressure contained in the attached male coupler, said piston means being positioned within said main cavity between said first and second ports and having a first surface against which fluid can impinge and a second surface which contacts a portion of said main valve means;
g) a stop positioned within said main cavity for limiting the movement of said main valve means towards said second port;
and h) flow check means for regulating fluid pressure acting on said first surface of said piston, said flow check means including a resilient ball positioned in said internal passage, said resilient ball having an outside diameter slightly larger than the inside diameter of said internal passage and less than the diameter of said recess, and first and second springs positioned in said internal passage between said first port and said ball and between said ball and said second port, respectively, said springs assisting in urging said ball back to a set position adjacent said recess once said ball has been displaced by fluid pressure, said ball being movable into alignment with said recess to relieve fluid pressure forces acting on said piston when fluid pressure acting on said second port side of said ball, plus the force of said second spring, is greater than fluid pressure acting on said first port side of said ball, plus the force of said first spring, thereby permitting said main valve means to move leftward assuring that an opening is established between said female coupler and said male coupler even when a vacuum is present in said main cavity.
7. The female coupler of claim 6 wherein said first spring has a higher spring force than said second spring.
8. The female coupler of claim 6 wherein a second recess is formed on the inner periphery of said internal passage in a spaced-apart relationship to said first recess and said ball is positioned approximately therebetween when said main valve means is closed.
9, The female coupler of claim 8 wherein said flow check means checks fluid flow in one direction at a pressure value which is less than the pressure value at which it relieves fluid pressure in an opposite direction.
10. The female coupler of claim 6 wherein a spring acts on said first surface of said piston means for urging said piston means and said main valve means towards said closed position.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US49151983A | 1983-05-04 | 1983-05-04 | |
| US491,519 | 1983-05-04 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1242226A true CA1242226A (en) | 1988-09-20 |
Family
ID=23952580
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000452053A Expired CA1242226A (en) | 1983-05-04 | 1984-04-16 | Flow check mechanism |
Country Status (5)
| Country | Link |
|---|---|
| JP (1) | JPS59208295A (en) |
| AU (1) | AU559996B2 (en) |
| BR (1) | BR8401980A (en) |
| CA (1) | CA1242226A (en) |
| MX (1) | MX161151A (en) |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5656590A (en) * | 1979-10-15 | 1981-05-18 | Matsushita Electric Ind Co Ltd | Heat exchanger having fin |
| JPS5715395U (en) * | 1980-06-30 | 1982-01-26 |
-
1984
- 1984-04-06 AU AU26612/84A patent/AU559996B2/en not_active Ceased
- 1984-04-16 CA CA000452053A patent/CA1242226A/en not_active Expired
- 1984-04-27 BR BR8401980A patent/BR8401980A/en not_active IP Right Cessation
- 1984-04-27 MX MX20117184A patent/MX161151A/en unknown
- 1984-05-04 JP JP59090079A patent/JPS59208295A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| BR8401980A (en) | 1984-12-11 |
| MX161151A (en) | 1990-08-08 |
| AU559996B2 (en) | 1987-03-26 |
| JPS59208295A (en) | 1984-11-26 |
| AU2661284A (en) | 1984-11-08 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |