CN112682544A - Overload self-adaptive oil supply valve - Google Patents
Overload self-adaptive oil supply valve Download PDFInfo
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- CN112682544A CN112682544A CN202011552996.9A CN202011552996A CN112682544A CN 112682544 A CN112682544 A CN 112682544A CN 202011552996 A CN202011552996 A CN 202011552996A CN 112682544 A CN112682544 A CN 112682544A
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Abstract
The invention belongs to the field of fluid machinery, and relates to an overload self-adaptive oil supply valve. The valve comprises an upper shell, a lower shell, an inertia valve core, a spring, a plurality of sealing rings and the like. The flow guide core and the inertia valve core of the lower shell are internally provided with an inlet and an outlet of a flow channel valve, and the fluid pressure of the inlet and the outlet of the valve is balanced. The spring force, the friction resistance between the flow guide core and the inertia valve core, the resistance of fluid to the inertia valve core, the gravity of the inertia valve core and the overload inertia force of the inertia valve core are balanced. In an overload environment, the overload inertia force of the inertia valve core is responded through spring force, and the friction resistance between the diversion core and the inertia valve core and the resistance of fluid to the inertia valve core are balanced rapidly under the influence, so that the flow resistance and the flow capacity of the oil supply pipeline are adjusted.
Description
Technical Field
The invention belongs to the field of fluid machinery, and relates to an overload self-adaptive oil supply valve.
Background
Under the condition of overload flying, the aircraft oil supply and delivery system is affected by overload, the pressure and flow of fuel oil supplied to an inlet of an engine can fluctuate, and states such as overpressure and low pressure are generated in severe cases, even the oil supply and delivery is temporarily interrupted.
The mode of improving oil supply under overload condition includes raising the lift of oil supply pump, setting pressure regulating valve, overflow pressure regulating and limiting during zero negative overload and responding to the mode of raising oil supply pressure during positive overload; the cold parallel connection lift of the oil supply pipeline is higher than the normally closed overload oil supply pump of the oil supply pump, and the oil supply mode of the oil supply pump is opened after a larger positive overload signal is sensed; the oil supply pipeline is connected with a normally open overload oil supply pump with a higher lift than the oil supply pump in parallel, and is provided with a regulating valve, and the regulating valve is opened to supply oil after a larger positive overload signal is sensed; the capsule type soft oil tank which extrudes fuel oil by depending on air-entraining pressure is connected in parallel with the oil supply pipeline, and the oil supplementing mode is overridden when the oil supply pipeline is lower in oil supply pressure due to positive overload, and the like. Because these modes all increase independent overload fuel feeding or pressure regulating device, have that additional weight is big, the energy consumption is high, and overload fuel feeding pipe opening seals the link many, can reduce the fuel feeding reliability.
Disclosure of Invention
The purpose of the invention is as follows: an overload adaptive fuel supply valve is provided for fuel supply regulation in a positive overload environment.
The technical scheme of the invention is as follows:
an overload adaptive fuel supply valve, comprising: the device comprises a lower shell 1, an upper shell 2, a spring 3, an inertia valve core 4, an inlet sealing ring 5, an inter-shell sealing ring 6, a glue pressing sealing ring 7, an outlet sealing ring 8, a flow guide core 9, a sliding bearing 10, a shaft 11, a flow guide hole 12, a pressure guide hole 13, a screw 14, a gasket 15, a connecting rib 16, a limiting step 17, an outlet connecting screw hole 18, an inlet connecting screw hole 19 and a spring mounting groove 20. The flow guide core 9 in the lower shell 1 is connected to the wall of the lower shell 1 through a connecting rib 16; a mounting groove 20 of the spring 3 is arranged in the flow guide core 9, a smooth cylindrical surface is processed in the flow guide core 9 to form a sliding bearing 10, and the axes of the mounting groove 20 and the sliding bearing 10 are parallel to the axis of the shell 1; the spring 3 is arranged in the spring mounting groove 20; the inertia valve core 4 is provided with a rubber pressing seal ring 7, the bottom of the inertia valve core 4 is processed with a smooth cylindrical surface to form a shaft 11, the inertia valve core 4 is arranged in a sliding bearing 10 and a compression spring 3 in the lower shell 1 through the sliding bearing; the inter-shell sealing ring 6 is embedded into a sealing ring groove of the upper shell 2, the upper shell 2 is connected with the lower shell 1 through a group of screws 14 and a group of gaskets 15, and the inter-shell sealing ring 6 is compressed to form sealing between the upper shell 2 and the lower shell 1; the upper shell 2 contacts the rubber pressing seal ring 7 to push the inertia valve core 4 to move downwards and compress the spring 3, and the spring force is transmitted to compress the rubber pressing seal ring 7 through the inertia valve core 4 to form the seal of the upper shell 2 and the inertia valve core 4; an inlet sealing ring 5 is embedded in an inlet sealing ring groove of the lower shell 1, and an inlet connecting screw hole 19 and an inlet pipeline are connected through a bolt to form connection and sealing; an outlet sealing ring 8 is embedded in an outlet sealing ring groove of the upper shell 2, and is connected with an outlet connecting screw hole 18 and an outlet pipeline through a bolt to form connection and sealing. The lower end of the lower shell 1 is a fluid inlet, and the upper end of the upper shell 2 is a fluid outlet; the flow guide hole 12 is connected with the pressure guide hole 13 and is communicated with the fluid inlet of the lower shell 1 and the fluid outlet of the upper shell 2; the limiting step 17 limits the maximum displacement of the diversion core 9 under the action of positive overload.
The elastic coefficient of the spring 3 is k, the compression amount of the spring 3 is x, the elastic force of the spring 3 is marked as F, and F is-kx; the sum of the frictional resistance between the shaft 11 and the sliding bearing 10 and the flow resistance of the fluid to the inertia valve core 4 is viscous resistance f, the resistance coefficient of the viscous resistance is c, the moving speed is V, and the viscous resistance f is-cV; the mass of the inertia valve core 4 is m, the self weight is recorded as G, G is mg, and G is the gravity acceleration; the overload coefficient is n, the overload force of the inertia valve core 4 is recorded as L, L is nG, the inertia valve core 4 is in a fully closed state, and the compression amount x of the spring 3 is0Initial opening overload factor of n0Initial compression x of spring 30＝-(mg+n0G) K is; spring 3 compression x in fully open state of inertia valve core 4m0The minimum overload coefficient of the full open is nm0L + G ═ F, i.e. satisfies (n)m0+1)G＝-kxm0The spring 3 has a spring constant k ═ nm0-n0)G/(xm0-x0)。
Furthermore, a flow guide hole 12 is formed in the flow guide core 9 to communicate the inner cavity of the sliding bearing 10 with a fluid inlet of the lower shell 1; the inertia valve core 4 and the shaft 11 thereof are internally provided with pressure guiding holes 13; the guide hole 12, the inner cavity of the sliding bearing 10 and the pressure guide hole 13 form a passage which is communicated with the fluid inlet of the lower shell 1 and the fluid outlet of the upper shell 2, pressure is balanced, and the small-flow normally open state of the inertia valve is kept.
The inner wall of the shell of the lower shell 1 is provided with a diversion hole 12, the inner wall of the shell of the upper shell 2 is provided with a pressure guiding hole 13, the diversion hole 12 and the pressure guiding hole 13 are communicated with the fluid inlet of the lower shell 1 and the fluid outlet of the upper shell 2, pressure is balanced, and the small-flow normally open state of the inertia valve is kept.
The diversion hole 12 is connected to the pressure guiding hole 13 through an external drainage tube 21, and is communicated with the fluid inlet of the lower shell 1 and the fluid outlet of the upper shell 2, so that the pressure is balanced, and the small-flow normally open state of the inertia valve is kept.
The inertia valve core 4 is a mushroom-shaped entity, and a glue pressing sealing ring 7 arranged on the outer surface of a mushroom head of the inertia valve core is in sealing fit with the inner wall of the upper shell 2; the outer surface of the mushroom head of the inertia valve core 4 is in streamline smooth transition, so that the over-current resistance is reduced. The flow guide core 9 is a mushroom-shaped entity, and the outer surface of the mushroom head of the flow guide core is in streamline smooth transition, so that the flow resistance is reduced; the flow guide core 9 is internally provided with a sliding bearing 10.
The number of the connecting ribs 16 is not less than 2, and the connecting ribs are uniformly distributed along the circumference of the axis of the lower shell 1.
The included angle alpha of a certain hole position of the inlet connecting screw hole 19 or the outlet connecting screw hole 18 is larger or smaller than the included angle alpha between the uniformly distributed mounting holes by more than 5 degrees, and the rest of the inlet connecting screw holes (19) are uniformly distributed on the circumference to prevent mounting errors.
The flow guide core 9 is provided with at least 2 flow guide holes 12 so as to increase the flow area, improve the flow and reduce the action response resistance.
When a group of not less than 3 spring mounting grooves 20 which are uniformly distributed along the axis of the flow guide core 9 are arranged in the flow guide core 9, a group of springs 3 with the same number as the spring mounting grooves 20 are correspondingly mounted; or when the flow guide core 9 is internally provided with 1 spring installation groove 20 which is coaxial with the axis of the flow guide core 9, 1 spring 3 is correspondingly installed. When 1 spring installation groove 20 which is coaxial with the axis of the diversion core 9 is inconvenient to arrange in the diversion core 9, the grouped spring installation grooves 20 are used.
The spring 3 is a conical spring or a cylindrical spring.
The surface roughness of the inner cavity of the upper shell 2 and the part of the rubber pressing sealing ring 7 is better than that of other parts of the inner cavity of the upper shell 2.
In an overload environment, the spring force responds to the overload inertia force of the inertia valve core 4 and is rapidly balanced under the influence of the friction resistance of the sliding bearing 10 and the shaft 11 and the viscous resistance of the fluid to the inertia valve core 4. In order to improve the response performance, a diversion hole 12 is formed in the diversion core 9 to reduce the flow resistance of the inner cavity of the discharge or suction sliding bearing 10; the surface of the shaft 11 and the cylindrical surface of the inner cavity of the sliding bearing 10 are processed smoothly or coated with lubricating materials, so that the friction resistance of the shaft of the flow guide core and the inertia valve core and a sliding friction pair of the bearing is reduced. The limiting step 17 limits the maximum displacement of the diversion core 9 under the action of positive overload.
The invention has the beneficial effects that: the invention can be used for supplying oil in the normal overload environment, simplifies the overload oil supply adjusting device, reduces the weight and improves the overload oil supply response and reliability. The engine can be widely applied to the normal overload environment oil supply of various aircrafts including airplanes, helicopters, rockets and the like.
Description of the drawings:
fig. 1 is an overload adaptive fuel supply valve according to the present invention.
Fig. 2 is an outline view of an overload adaptive fuel supply valve according to the present invention.
Fig. 3 is a view of the inlet end of an overload adaptive fuel supply valve according to the present invention.
Fig. 4 is a view of the outlet end of an overload adaptive fuel supply valve according to the present invention.
Fig. 5 is a view showing the full opening of an overload adaptive fuel supply valve in response to an overload according to the present invention.
Fig. 6 is a schematic view illustrating a guide core of an overload adaptive fuel supply valve according to the present invention having a plurality of guide holes.
FIG. 7a is a schematic view showing the distribution of the flow in the fully closed state of the overload adaptive fuel supply valve according to the present invention
FIG. 7b is a schematic view showing the distribution of the fluid in the half-open state of the overload adaptive fuel supply valve according to the present invention
FIG. 7c is a schematic view showing the distribution of the flow in the fully opened state of the overload adaptive fuel supply valve according to the present invention
FIG. 7d is a schematic view showing the distribution of the fluid in the fully opened state when the flow guide core of the overload adaptive fuel supply valve has a plurality of flow guide holes according to the present invention
FIG. 8 is a simulation modeling block diagram of the performance of an overload adaptive fuel delivery valve of the present invention.
FIG. 9 is an overload adaptive fuel supply valve using an external drainage tube
1-lower shell, 2-upper shell, 3-spring, 4-inertia valve core, 5-inlet sealing ring, 6-inter-shell sealing ring, 7-glue pressing sealing ring, 8-outlet sealing ring, 9-flow guide core, 10-sliding bearing, 11-shaft, 12-flow guide hole, 13-pressure guide hole, 14-screw, 15-gasket, 16-connecting rib, 17-limit step, 18-outlet connecting screw hole, 19-inlet connecting screw hole, 20-spring mounting groove, 21-drainage tube
Detailed Description
Referring to fig. 1, the present invention provides an overload adaptive fuel supply valve, including: the device comprises a lower shell 1, an upper shell 2, a spring 3, an inertia valve core 4, an inlet sealing ring 5, an inter-shell sealing ring 6, a glue pressing sealing ring 7, an outlet sealing ring 8, a flow guide core 9, a sliding bearing 10, a shaft 11, a flow guide hole 12, a pressure guide hole 13, a screw 14, a gasket 15, a connecting rib 16, a limiting step 17, an outlet connecting screw hole 18, an inlet connecting screw hole 19 and a spring mounting groove 20, wherein the flow guide hole 12 adopts a mode of passing through the flow guide core 9, and the pressure guide hole 13 adopts a mode of penetrating through the inertia valve core 4 and the shaft 11; the flow guide core 9 in the lower shell 1 is connected to the wall of the lower shell 1 through a connecting rib 16; a mounting groove 20 of the spring 3 is arranged in the flow guide core 9, a smooth cylindrical surface is processed in the flow guide core 9 to form a sliding bearing 10, and the axes of the mounting groove 20 and the sliding bearing 10 are parallel to the axis of the shell 1; the spring 3 is arranged in the spring mounting groove 20; the inertia valve core 4 is provided with a rubber pressing seal ring 7, the bottom of the inertia valve core 4 is processed with a smooth cylindrical surface to form a shaft 11, a pressure guiding hole 13 is arranged in the shaft, and the inertia valve core 4 is arranged in a sliding bearing 10 and a compression spring 3 in the lower shell 1 through the sliding bearing; the inter-shell sealing ring 6 is embedded into a sealing ring groove of the upper shell 2, the upper shell 2 and the lower shell 1 are installed through a group of screws 14 and a group of gaskets 15, and the inter-shell sealing ring 6 is compressed to form sealing between the upper shell 2 and the lower shell 1; the upper shell 2 contacts the rubber pressing seal ring 7 to push the inertia valve core 4 to move downwards and compress the spring 3, and the spring force is transmitted to compress the rubber pressing seal ring 7 through the inertia valve core 4 to form the seal of the upper shell 2 and the inertia valve core 4; an inlet sealing ring 5 is embedded in an inlet sealing ring groove of the lower shell 1, and an inlet connecting screw hole 19 and an inlet pipeline are connected through a bolt to form connection and sealing; an outlet sealing ring 8 is embedded in an outlet sealing ring groove of the upper shell 2 and passes through a screwThe bolt connects the outlet connection screw 18 with the outlet line, forming a connection and seal. The lower end of the lower shell 1 is a fluid inlet, and the upper end of the upper shell 2 is a fluid outlet. A flow guide hole 12 is formed in the flow guide core 9 and communicates the inner cavity of the sliding bearing 10 with a fluid inlet of the lower shell 1; the guide hole 12, the inner cavity of the sliding bearing 10 and the guide pressure hole 13 form a passage, so that the fluid inlet of the lower shell 1 is communicated with the fluid outlet of the upper shell 2, and the fluid pressure of the inlet and the outlet of the valve is balanced. The assembled profile is shown in fig. 2, with the inlet end shown in fig. 3 and the outlet end shown in fig. 4. The limiting step 17 limits the maximum displacement of the guide core 9 under the action of positive overload, and the state after the guide core is in place is shown in fig. 5. The elastic coefficient of the spring 3 is k, the compression amount of the spring 3 is x, the elastic force of the spring 3 is marked as F, and F is-kx; the sum of the frictional resistance between the shaft 11 and the sliding bearing 10 and the flow resistance of the fluid to the inertia valve core 4 is viscous resistance f, the resistance coefficient of the viscous resistance is c, the moving speed is V, and the viscous resistance f is-cV; the mass of the inertia valve core 4 is m, the self weight is recorded as G, G is mg, and G is the gravity acceleration; the overload coefficient is n, the overload force of the inertia valve core 4 is recorded as L, L is nG, the inertia valve core 4 is in a fully closed state, and the compression amount x of the spring 3 is0Initial opening overload factor of n0Initial compression x of spring 30＝-(mg+n0G) K is; spring 3 compression x in fully open state of inertia valve core 4m0The minimum overload coefficient of the full open is nm0L + G ═ F, i.e. satisfies (n)m0+1)G＝-kxm0The spring 3 has a spring constant k ═ nm0-n0)G/(xm0-x0)。N≥nm0When in use, the inertia valve core 4 is fully opened.
Furthermore, a flow guide hole 12 is formed in the flow guide core 9 to communicate the inner cavity of the sliding bearing 10 with a fluid inlet of the lower shell 1; the inertia valve core 4 and the shaft 11 thereof are internally provided with pressure guiding holes 13; the guide hole 12, the inner cavity of the sliding bearing 10 and the pressure guide hole 13 form a passage which is communicated with the fluid inlet of the lower shell 1 and the fluid outlet of the upper shell 2, pressure is balanced, and the small-flow normally open state of the inertia valve is kept.
The inner wall of the shell of the lower shell 1 is provided with a diversion hole 12, the inner wall of the shell of the upper shell 2 is provided with a pressure guiding hole 13, the diversion hole 12 and the pressure guiding hole 13 are communicated with the fluid inlet of the lower shell 1 and the fluid outlet of the upper shell 2, pressure is balanced, and the small-flow normally open state of the inertia valve is kept.
The diversion hole 12 is connected to the pressure guiding hole 13 through an external drainage tube 21, and is communicated with the fluid inlet of the lower shell 1 and the fluid outlet of the upper shell 2, so that the pressure is balanced, and the small-flow normally open state of the inertia valve is kept.
The inertia valve core 4 is a mushroom-shaped entity, and a glue pressing sealing ring 7 arranged on the outer surface of a mushroom head of the inertia valve core is in sealing fit with the inner wall of the upper shell 2; the outer surface of the mushroom head of the inertia valve core 4 is in streamline smooth transition, so that the over-current resistance is reduced. The flow guide core 9 is a mushroom-shaped entity, and the outer surface of the mushroom head of the flow guide core is in streamline smooth transition, so that the flow resistance is reduced; the flow guide core 9 is internally provided with a sliding bearing 10.
The number of the connecting ribs 16 is not less than 2, and the connecting ribs are uniformly distributed along the circumference of the axis of the lower shell 1.
The included angle alpha of a certain hole position of the inlet connecting screw hole 19 or the outlet connecting screw hole 18 is larger or smaller than the included angle alpha between the uniformly distributed mounting holes by more than 5 degrees, and the rest of the inlet connecting screw holes (19) are uniformly distributed on the circumference to prevent mounting errors.
As shown in fig. 6, the diversion core 9 has no less than 2 diversion holes 12 to increase the flow area, improve the flow and reduce the action response resistance.
When a group of not less than 3 spring mounting grooves 20 which are uniformly distributed along the axis of the flow guide core 9 are arranged in the flow guide core 9, a group of springs 3 with the same number as the spring mounting grooves 20 are correspondingly mounted; or when the flow guide core 9 is internally provided with 1 spring installation groove 20 which is coaxial with the axis of the flow guide core 9, 1 spring 3 is correspondingly installed. When 1 spring installation groove 20 which is coaxial with the axis of the diversion core 9 is inconvenient to arrange in the diversion core 9, the grouped spring installation grooves 20 are used.
The spring 3 is a conical spring or a cylindrical spring.
The surface roughness of the inner cavity of the upper shell 2 and the part of the rubber pressing sealing ring 7 is better than that of other parts of the inner cavity of the upper shell 2.
In an overload environment, the spring force responds to the overload inertia force of the inertia valve core 4 and is rapidly balanced under the influence of the friction resistance of the sliding bearing 10 and the shaft 11 and the viscous resistance of the fluid to the inertia valve core 4. Fig. 7a, 7b and 7c show the flow field states of the inertia valve of the present invention when fully closed, half opened and fully opened, respectively, with fluid in the shaded portions. In order to improve the response performance, the diversion hole 12 is opened in the diversion core 9 to reduce the flow resistance when the fluid is discharged or sucked into the inner cavity of the sliding bearing 10, and fig. 7d shows the flow field state when the inertia valve with a plurality of diversion holes 12 is fully opened, and the shaded part is the fluid. The surface of the shaft 11 and the cylindrical surface of the inner cavity of the sliding bearing 10 are processed smoothly or coated with lubricating materials, so that the friction resistance of the shaft of the flow guide core and the inertia valve core and a sliding friction pair of the bearing is reduced. The limiting step 17 limits the maximum displacement of the diversion core 9 under the action of positive overload.
FIG. 8 is a simulation modeling block diagram of the performance of the overload adaptive fuel delivery valve of the present invention.
Examples of applications of the invention: the inlet drift diameter of the lower shell 1 is 28mm, the outlet drift diameter of the upper shell 2 is 28mm, and the flow passage areas of the lower shell 1 and the upper shell 2 are approximately equal; the bearing 10 is an aluminum piece, and the surface roughness is Ra0.8; the shaft 11 is a steel part, and the surface roughness is Ra0.4; the weight of the inertia valve core 4 is 0.1kg, and the initial opening overload is 1G; limiting overload is 3G, and the viscous resistance coefficient is 0.3 in an aviation kerosene environment at the temperature of 20 ℃; the spring 3 is a cylindrical spring, the elastic force is 0.2N/mm, the distance between the inertia valve core 4 and the limit step 17 from the closed position is 10mm, and the elastic force and the compression amount of the spring 3 are linear in the space. When the flying overload is increased to 3.5G from 0 in 0.7 second, the inertia valve core 4 is opened instantly when the overload reaches 1G, the inertia valve core is increased to a limit position when the overload continues to reach 3G, the overload lasts for 4 seconds, then the inertia valve core 4 is reduced to 0 from 3.5G in 0.7 second, the inertia valve core is closed instantly when the overload falls to 3G, and the inertia valve core is closed when the overload falls to 1G. When the flying overload is increased from 0 to 2.5G within 0.5 second, the inertia valve core 4 is opened instantly when the overload reaches 1G, continuously overshoots to 2.5G and reaches a static opening position of 2.61G, then rebounds and oscillates in a small amplitude for a plurality of cycles, wherein the cycle is 0.141 second, the maximum amplitude is 0.44mm, the overload of 2.5G lasts for 3 seconds, then is reduced from 2.5G to 0 within 0.5 second, and is closed when the overload is reduced to 1G.
Fig. 9 shows an overload adaptive oil supply valve using an external drainage tube, in which a diversion hole 12 is connected to a pressure guide hole 13 through an external drainage tube 21, and a fluid inlet of a lower housing 1 and a fluid outlet of an upper housing 2 are connected in a penetrating manner.
Claims (10)
1. An overload adaptive fuel supply valve, comprising: a lower shell (1), an upper shell (2), a spring (3), an inertia valve core (4), an inlet sealing ring (5), an inter-shell sealing ring (6), a glue pressing sealing ring (7), an outlet sealing ring (8), a flow guide core (9), a sliding bearing (10), a shaft (11), a flow guide hole (12), a pressure guide hole (13), a screw (14), a gasket (15), a connecting rib (16), a limiting step (17), an outlet connecting screw hole (18), an inlet connecting screw hole (19) and a spring mounting groove (20),
wherein, the flow guide core (9) in the lower shell (1) is connected to the wall of the lower shell (1) through a connecting rib (16); an installation groove (20) of the spring (3) is arranged in the flow guide core (9), a smooth cylindrical surface is processed in the flow guide core (9) to form a sliding bearing (10), and the axes of the installation groove (20) and the sliding bearing (10) are parallel to the axes of the shell (1) and the flow guide core (9); the spring (3) is arranged in the spring mounting groove (20); the inertia valve core (4) is provided with a rubber pressing sealing ring (7), the bottom of the inertia valve core (4) is processed with a smooth cylindrical surface to form a shaft (11), and the inertia valve core (4) is arranged in a sliding bearing (10) and a compression spring (3) in the lower shell (1) through the sliding bearing; the sealing ring (6) between the shells is embedded into a sealing ring groove of the upper shell (2), the upper shell (2) and the lower shell (1) are installed through a group of screws (14) and a group of gaskets (15), and the sealing ring (6) between the shells is compressed to form sealing between the upper shell (2) and the lower shell (1); the upper shell (2) is in contact with the rubber pressing sealing ring (7) to push the inertia valve core (4) to move downwards and compress the spring (3), and the spring force is transmitted through the inertia valve core (4) to compress the rubber pressing sealing ring (7) to form the sealing of the upper shell (2) and the inertia valve core (4); an inlet sealing ring (5) is embedded in an inlet sealing ring groove of the lower shell (1), and an inlet connecting screw hole (19) and an inlet pipeline are connected through an inlet mounting bolt to form connection and sealing; an outlet sealing ring (8) is embedded in an outlet sealing ring groove of the upper shell (2), and an outlet connecting screw hole (18) and an outlet pipeline are connected through an outlet mounting bolt to form connection and sealing. The lower end of the lower shell (1) is a fluid inlet, and the upper end of the upper shell (2) is a fluid outlet; the flow guide hole (12) is connected with the pressure guide hole (13) and is communicated with the fluid inlet of the lower shell (1) and the fluid outlet of the upper shell (2); the limiting step (17) limits the maximum displacement of the diversion core (9) under the action of positive overload.
2. The overload adaptive oil supply valve according to claim 1, wherein a flow guide hole (12) is formed in the flow guide core (9) to communicate the inner cavity of the sliding bearing (10) with a fluid inlet of the lower shell (1); pressure guide holes (13) are formed in the inertia valve core (4) and the shaft (11), and a passage is formed by the flow guide holes (12), the inner cavity of the sliding bearing (10) and the pressure guide holes (13) and is communicated with the fluid inlet of the lower shell (1) and the fluid outlet of the upper shell (2).
3. The overload adaptive oil supply valve according to claim 1, wherein the lower shell (1) is provided with a diversion hole (12) on the inner shell wall, the upper shell (2) is provided with a pressure guide hole (13) on the inner shell wall, and the diversion hole (12) and the pressure guide hole (13) are communicated to connect the lower shell (1) fluid inlet and the upper shell (2) fluid outlet.
4. The overload adaptive oil supply valve according to claim 1, wherein the diversion hole (12) is communicated with the pressure guide hole (13) through an external drainage pipe (21) to connect the fluid inlet of the lower shell (1) and the fluid outlet of the upper shell (2).
5. The overload self-adaptive oil supply valve according to claim 1, wherein the flow guide core (9) and the inertia valve core (4) are mushroom-head-shaped solid bodies, and the outer surface of each mushroom head is in streamline smooth transition; the mushroom head of the inertia valve core (4) is provided with a rubber pressing seal ring (7), and a sliding bearing (10) is arranged in the flow guide core (9).
6. The overload self-adaptive oil supply valve according to claim 1, wherein the number of the connecting ribs (16) is not less than 2, and the connecting ribs are uniformly distributed along the circumference of the axis of the lower shell (1).
7. The overload self-adaptive oil supply valve according to claim 1, wherein an included angle of a hole position of the inlet connecting screw hole (19) or the outlet connecting screw hole (18) is alpha, the other inlet connecting screw holes (19) are uniformly distributed on the circumference, and the alpha is 5 degrees larger or smaller than the included angle between the uniformly distributed mounting holes.
8. The overload adaptive oil supply valve according to claim 1, wherein the guide core (9) has not less than 2 guide holes (12).
9. The overload self-adaptive oil supply valve according to claim 1, wherein the flow guide core (9) is internally provided with a group of not less than 3 spring installation grooves (20) which are uniformly distributed along the axis of the flow guide core (9), and a group of springs (3) with the same number as the spring installation grooves (20) are correspondingly installed; or the flow guide core (9) is internally provided with 1 spring installation groove (20) which is coaxial with the axis of the flow guide core (9) and is correspondingly provided with 1 spring (3).
10. Overload adaptive fuel supply valve according to claim 1, characterised in that the spring (3) is a conical spring or a cylindrical spring.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011552996.9A CN112682544B (en) | 2020-12-24 | 2020-12-24 | Overload self-adaptive oil supply valve |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202011552996.9A CN112682544B (en) | 2020-12-24 | 2020-12-24 | Overload self-adaptive oil supply valve |
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| CN112682544A true CN112682544A (en) | 2021-04-20 |
| CN112682544B CN112682544B (en) | 2023-01-24 |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4313462A (en) * | 1980-10-10 | 1982-02-02 | Grove Valve And Regulator Company | Sequentially operated valve structure |
| CN103429940A (en) * | 2010-12-07 | 2013-12-04 | Ta海卓尼克斯有限责任公司 | Improvement in balancing and control valve |
| CN105864469A (en) * | 2016-04-26 | 2016-08-17 | 苏州纽威阀门股份有限公司 | Axial-flow type check valve capable of replacing internal part on line |
| WO2019220153A2 (en) * | 2018-05-14 | 2019-11-21 | Hydromat D.O.O. | Axial valve of the modular concept of construction |
| CN210461807U (en) * | 2019-06-03 | 2020-05-05 | 欧电阀门集团有限公司 | Axial flow type check valve |
| CN111664273A (en) * | 2020-05-29 | 2020-09-15 | 江苏神通阀门股份有限公司 | Cryogenic axial flow check valve with online maintenance function |
-
2020
- 2020-12-24 CN CN202011552996.9A patent/CN112682544B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4313462A (en) * | 1980-10-10 | 1982-02-02 | Grove Valve And Regulator Company | Sequentially operated valve structure |
| CN103429940A (en) * | 2010-12-07 | 2013-12-04 | Ta海卓尼克斯有限责任公司 | Improvement in balancing and control valve |
| CN105864469A (en) * | 2016-04-26 | 2016-08-17 | 苏州纽威阀门股份有限公司 | Axial-flow type check valve capable of replacing internal part on line |
| WO2019220153A2 (en) * | 2018-05-14 | 2019-11-21 | Hydromat D.O.O. | Axial valve of the modular concept of construction |
| CN210461807U (en) * | 2019-06-03 | 2020-05-05 | 欧电阀门集团有限公司 | Axial flow type check valve |
| CN111664273A (en) * | 2020-05-29 | 2020-09-15 | 江苏神通阀门股份有限公司 | Cryogenic axial flow check valve with online maintenance function |
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