CN110953359B

CN110953359B - Multi-rotation type hydraulic valve

Info

Publication number: CN110953359B
Application number: CN201911407090.5A
Authority: CN
Inventors: 徐学新
Original assignee: Individual
Current assignee: Individual
Priority date: 2019-12-31
Filing date: 2019-12-31
Publication date: 2023-03-07
Anticipated expiration: 2039-12-31
Also published as: CN110953359A

Abstract

The utility model provides a many gyration formula hydraulic valve, includes hydraulic motor, speed reduction booster, valve drive mechanism, encoder, valve and connecting piece, can automatically regulated hydraulic motor output torque according to the change of valve at the in-process load of opening and close, realizes intelligent control mode, prevents to the vibrations of valve and assaults, and environmental suitability is strong, uses and can the reliable operation to the occasion of wide application electric valve and the operational environment homoenergetic that does not adapt to electric valve. The valve can be used in inflammable, explosive, damp, high-pollution and high-dust occasions, the risk is effectively avoided by adopting a method of arranging a hydraulic system in different places, the opening degree of the valve can be accurately controlled, and the valve core can be effectively and reliably self-locked. The encoder improves the control precision of the hydraulic valve in the operation process, improves the automatic control level, can realize necessary conditions of a wireless monitoring function, meets the industrialization requirement of the 5G era, and has an emergency manual operation function.

Description

Multi-rotation type hydraulic valve

Technical Field

The invention belongs to the field of valves, and particularly relates to a multi-rotation type hydraulic valve (a multi-rotation type hydraulic valve driven by a universal hydraulic motor).

Background

The valve is used as a key part in water, oil and gas medium pipeline transportation, and is widely applied to various fields of petroleum, natural gas, oil and gas wharfs, chemical engineering, ships, power stations, metallurgy, municipal administration and the like. In recent years, with the upsizing of engineering projects, the demand of large-diameter or large-size valves is increasing, and manual operation is very difficult and cannot meet the requirements of the times. In order to meet the requirements of an automated system, various valve driving methods have been developed, such as an electric valve driven by an electric motor or an accelerator, a pneumatic valve driven by an air cylinder, a hydraulic valve driven by a hydraulic oil cylinder, and the like. The driving mode still has some shortcomings and shortcomings in application practice, the electric valve still has small instant starting torque in development, application and improvement for many years, so that the valve is not reliably opened, the rotary inertia is large when the motor drives the speed reducer to operate, the impact on the valve is also large, the control precision of the electric valve is poor due to the fact that the motor does not have a self-locking function, and on the other hand, the electric valve is not suitable for being applied to flammable and explosive dangerous occasions such as petroleum and natural gas even though protection is carried out due to the fact that electric drive is adopted. The pneumatic valve has large volume, low air source pressure and small driving force on the valve, and the unstable operation of the valve can be caused by the compressibility of air. The hydraulic valve used at present is a valve driven by an oil cylinder, and the valve plate in the valve is difficult to self-lock due to the floatability of an oil cylinder piston, and the emergency manual operation is not easy to realize. On the other hand, the hydraulic valve is ultrahigh or ultra-wide in shape and size due to the stroke of the oil cylinder. In addition, several patents which are issued by the inventor of the patent in advance are that a hydraulic motor is used for directly driving a hydraulic valve, and the hydraulic valve is theoretically feasible and has obvious advantages. But the difficulty of manufacturing the special non-standard hydraulic motor is high, the processing cost is high, the manufacturing period is long, and the popularization and the application of the technology are not facilitated. With the coming of the 5G era, industrial automation requires higher control level of the valve, so that products with higher reliability, safety and control precision are needed, and a good foundation is laid for realizing wireless remote control.

Disclosure of Invention

The invention aims to provide a multi-rotation type hydraulic valve, which can be driven by a standard hydraulic motor, and can reduce the cost, shorten the manufacturing period and enable the technology to be popularized and serve the society as soon as possible on the basis of improving the reliability of the opening and closing process of the valve.

The technical scheme is as follows:

a multi-rotary hydraulic valve is composed of hydraulic motor and speed-reducing booster.

The method is characterized in that:

the deceleration booster includes a first small bevel gear and a large bevel gear that mesh with each other.

The first small bevel gear has a smaller diameter than the large bevel gear.

The output shaft of the transversely arranged hydraulic motor is fixedly connected with a transversely arranged first bevel pinion shaft.

The first bevel pinion shaft is supported within the gear housing by a first gear bearing.

The big bevel gear is arranged above the inner part of the gear box body.

The large bevel gear is connected with a power input part of the valve transmission mechanism.

The power input part of the valve transmission mechanism is a vertically arranged valve driving shaft sleeve which is fixedly connected with a large bevel gear.

The valve transmission mechanism comprises a valve driving shaft sleeve, a lifting valve rod nut and a lifting valve rod.

The upper end of the valve driving shaft sleeve penetrates through the gear box body and is inserted into an upper rolling bearing embedded in an upper rolling bearing seat, and the upper rolling bearing seat is fixed on the gear box body.

The lifting valve rod penetrates through the upper rolling bearing seat and downwards penetrates through the valve driving shaft sleeve to be in threaded fit with the lifting valve rod nut.

A position indication scale protective cover is fixed above the upper rolling bearing seat.

The side surface of the position indication scale protective cover is provided with a pointer pointing guide opening, and two sides of the position indication scale protective cover are provided with length scales.

The upper end surface of the lifting valve rod is fixed with a valve lifting position pointer, and the corresponding pointer points to the guide port.

The lower end of the valve driving shaft sleeve is fixed with the lifting valve rod nut.

The upper end face of an annular boss on the middle part of the outer surface of the lifting valve rod nut is provided with an upper thrust bearing, the lower end face of the annular boss is provided with a lower thrust bearing, the upper thrust bearing is arranged in the inserted valve rod nut rolling bearing seat, the lower end part of the lower thrust bearing is provided with a bearing clearance adjusting and fixing flange, and the lower end of the lifting valve rod nut is embedded into a lower rolling bearing in the lower rolling bearing seat.

The inserted valve rod nut rolling bearing seat, the bearing gap adjusting fixing flange and the lower rolling bearing seat are fixedly connected with the gear box body.

The large bevel gear placed above is meshed with a second small bevel gear transversely arranged in the gear box body. The diameter of the second small bevel gear is smaller than that of the large bevel gear.

The second bevel pinion shaft is supported on the right side in the gear box body through a second gear bearing.

And an emergency operation device and an encoder are arranged at the right end of the shaft of the second bevel pinion.

And a left bearing and a right bearing are arranged on the part of the second bevel pinion, which is positioned on the right outer side of the gear box body.

Mounting holes of two side plates of the emergency manual operation handle body with an internal U-shaped space are respectively arranged on the left bearing outer ring and the right bearing outer ring.

A left ratchet wheel and a right ratchet wheel (a pair of ratchet wheels) with opposite ratchet directions are fixed on a second bevel pinion shaft between the left bearing and the right bearing.

The pawl and the reset spring fixed pin that transversely set up are fixed to be worn to establish on emergent manual operation handle body to the cover is equipped with left pawl and right pawl, overlaps between and establishes reset spring.

One end of the reset spring is clamped at the groove of the left pawl handle, the other end of the reset spring is clamped at the groove of the right pawl handle, and the reset spring is set to be spring force so that the left pawl and the right pawl are close to each other towards the axis direction of the second bevel pinion.

The left pawl is provided with a left pawl pin hole corresponding to the left through hole of the emergency manual operation handle body, and the left pawl pin hole and the left through hole are arranged in such a way that a left pawl clutch bolt is inserted and fixed between the left pawl pin hole and the left through hole when the left pawl is outwards broken to separate the left pawl and enable the left pawl to be separated from the left ratchet wheel.

And a right pawl pin hole is formed in the right pawl and corresponds to a right through hole of the emergency manual operation handle body, and the right pawl pin hole and the right through hole are arranged to be used for outwards opening the right pawl so that a right pawl clutch bolt is inserted and fixed between the right pawl pin hole and the right through hole when the right pawl is separated from the right ratchet wheel.

And a left pawl elastic sleeve is arranged between the left pawl and the pawl and between the left pawl and the reset spring fixing pin.

And a right pawl elastic sleeve is arranged between the right pawl and the pawl and between the right pawl and the reset spring fixing pin.

The valve transmission mechanism comprises a non-rising stem valve driving valve rod which is vertically arranged, and the non-rising stem valve driving valve rod is used as a power input part of the valve transmission mechanism.

The upper end of a non-rising stem valve driving valve rod is fixedly connected with a large bevel gear.

The lower end of the non-rising stem valve driving valve rod is provided with a lower valve rod rolling bearing which is fixedly supported on the inner side of the gear box body through a lower valve rod rolling bearing seat.

The upper end of the non-rising stem valve driving valve rod is provided with an upper valve rod rolling bearing, and the non-rising stem valve driving valve rod is fixedly supported outside the upper part of the gear box body through an upper valve rod rolling bearing seat.

An encoder is arranged on the upper end surface of the non-rising stem valve driving valve rod.

The second small bevel gear transversely arranged in the gear box body is meshed with the large bevel gear placed above. The diameter of the second small bevel gear is smaller than that of the large bevel gear.

And the second bevel pinion shaft is positioned at the right outer side of the gearbox body and is fixed with a manual emergency turntable of an emergency operation device.

The advantages are that:

the large-torque hydraulic motor is adopted to drive the speed reduction booster to drive the valve, so that the reliability of the opening process of the valve is improved.

The hydraulic motor is used as a power element, and a special non-standard hydraulic motor for the production of the hydraulic motor is avoided. The speed reduction booster can be selected from various known standard hydraulic motors, so that the manufacturing cost of the multi-rotation hydraulic valve is reduced, the manufacturing period is shortened, and the specialized serial production is facilitated.

The output torque of the hydraulic motor is automatically adjusted through a hydraulic control system according to the load change of the valve in the opening and closing process, and an ideal intelligent control mode is realized. Therefore, the impact and vibration to the valve in the operation process of the driving device are reduced, and the safety and the reliability of the valve operation are improved.

The multi-rotation type hydraulic valve has strong adaptability to the environment, can be used in the occasions where the electric valve is widely applied and the working environment which is not suitable for the electric valve, and can reliably operate. The hydraulic system can be used in inflammable, explosive, humid, high-pollution and high-dust occasions, effectively avoids risks by arranging the hydraulic system in different places, can work safely and reliably, and can realize remote automatic control.

The multi-rotation type hydraulic valve overcomes the inertia error generated by the driving of a motor in the operation process of the electric valve and the self-locking defect of the valve driven by a hydraulic oil cylinder, and can realize the effective and reliable self-locking of the valve core.

The encoder is adopted to improve the control precision of the hydraulic valve in the operation process and improve the automation control level, is a necessary condition for realizing the wireless monitoring function, and is suitable for the industrialization requirement of the 5G era.

The valve rod nut transmission mechanism is inserted into the speed reduction booster in a bearing seat mode, so that the size and the height dimension of the multi-rotation type hydraulic valve are reduced.

The multi-turn hydraulic valve is provided with a rocker type handle which is formed by a ratchet wheel and pawl mechanism and is suitable for the operation of large-specification valves, so that the multi-turn hydraulic valve is convenient and labor-saving to operate and has an emergency manual operation function.

Drawings

Fig. 1 is a sectional view of embodiment 1 of the present invention.

Fig. 2 is a partially enlarged view of fig. 1.

Fig. 3 is a partially enlarged view of a portion of the emergency operation device of fig. 1.

Fig. 4 is a schematic structural diagram of the connection between the embodiment 1 and the rising stem valve.

Fig. 5 is a cross-sectional view C-C of fig. 3. (the left pawl is broken off to the right side, the left pawl is disengaged from the left ratchet wheel).

Fig. 6 is a cross-sectional view taken along line D-D of fig. 3. (the right pawl has been broken to the left, and the right pawl is disengaged from the right ratchet wheel).

Fig. 7 is a cross-sectional view E-E of fig. 3.

FIG. 8 is a sectional view of example 2.

Fig. 9 is a schematic view of the structure of the embodiment 2 matched with the hidden rod valve.

Fig. 10 is a diagram of a hydraulic system and an assembly schematic of the present valve (where the hydraulic system is known in the art).

Fig. 11 is a perspective view showing an assembly structure of the return spring, two ratchets and pawls, and the return spring fixing pins.

1. <xnotran> , 2. , 3. , 4. , 5., 6. , 7. , 8. , 9. , 10. , 11. , 12. , 13. , 14. , 15. , 16. , 17. , 18. , 19. , 20. , 21. , 22. , 23. , 24. , 25. , 26. , 27., 28. , 29. , 30. , 31. , 32. , 33. , 34. , 35. , 36. , 37. , 38. , 39. , 40. , 41. , 42. , 43. , 44. , 45. , 46. , 47. 48. , 49. , 50. , 51. , 52. , 53. , 54. , 55. , 56. , 57. , </xnotran> 58. The valve comprises a flat key, 59, a pointer pointing guide port, 60, an annular boss, 61, a left pawl elastic sleeve, 62, a right ratchet wheel, 63, a left pawl clutch bolt, 64, a spacing groove, 65, a left pawl handle, 66, a right pawl handle, 67, a second through hole, 68, a left pawl pin hole, 69, a right pawl pin hole, 70, a first through hole, 71, a left ratchet wheel, 72, a right pawl, 73, a ratchet wheel groove, 74, a right pawl groove, 75, a left pawl groove and 76, and a hidden rod valve drives a valve rod connecting key.

Detailed Description

Example 1

A multi-rotation type hydraulic valve has a hydraulic motor 1. The hydraulic motor 1 is a flexible and reliable matched product for the selection of known standard series products, the supply period of the hydraulic valve can be shortened, the price of the product can be reduced, the standardized serialization of the product is convenient, the direct drive of the hydraulic motor for the known multi-turn hydraulic valve is overcome, the hydraulic motor is theoretically feasible and has remarkable advantages, but the design and manufacturing difficulty is large, the construction period is long, the processing cost is high, the standardization degree is low, and the popularization and the application of the advantage technology of the multi-turn hydraulic valve are not facilitated.

The three patents which were granted by the inventor, namely 201210158229.9 multi-rotation type hydraulic valve, 200610135071.8 rotation type hydraulic valve and 200610135142.4 rotation type hydraulic valve, wherein the required hydraulic motor needs to be independently tailored and processed, the production period is long, and the applied hydraulic motor 1 adopts standard series products, so that the production and supply period is short, and the use is more convenient.

In the present embodiment, the hydraulic motor 1 is a hydraulic plug motor, and the torque of the hydraulic motor is large.

The side surface of the hydraulic motor is provided with an oil inlet and outlet A, an oil inlet and outlet B and an oil drainage port L.

The first three-way joint 4 is arranged at the oil inlet and outlet A, the first end of the first three-way joint 4 is connected with the oil inlet and outlet A, and the second end is connected with an oil port of a hydraulic system.

And a second three-way joint 3 is arranged at the oil inlet and outlet B, the first end of the second three-way joint 3 is connected with the oil inlet and outlet B, and the second end is connected with the other oil port of the hydraulic system.

A hydraulic ball valve 2 (a manual high-pressure hydraulic ball valve) is connected between the third head of the first three-way joint 4 and the third head of the second three-way joint 3. Realizes the connection and disconnection between the oil inlet and outlet A and the oil inlet and outlet B, is used for emergency manual operation,

and the oil drainage port L is connected to a corresponding oil port of the hydraulic system.

The power output (output shaft) of the hydraulic motor 1 is connected with the power input (first bevel pinion 9) of the deceleration booster.

The power output of the deceleration booster (large bevel gear 46) is connected with the power input of the valve transmission mechanism (valve driving shaft sleeve 43).

The reduction booster comprises a first small bevel gear 9 and a large bevel gear 46 which mesh with each other.

The first small bevel gear 9 is smaller in diameter than the large bevel gear 46.

An output shaft of a hydraulic motor 1 which is transversely arranged at the left outer side of a gear box body 8 is connected with a first small bevel gear 9 shaft which is transversely arranged through a coupler 5.

The two sides of the motor and gear box connecting body 6 are respectively fixedly connected with a shell of the hydraulic motor 1 and a gear box body 8. The end surface of the motor and gear box connecting body 6 is provided with a boss for pressing a left bearing 7 of the first gear.

The coupling 5 is arranged in a motor-gearbox coupling body 6.

The first bevel pinion 9 shaft is supported in the gear housing 8 by first gear bearings (a first gear left bearing 7 and a first gear right bearing 47).

The shaft root of the first bevel pinion 9 is provided with a boss which presses the right bearing 47 of the first pinion.

The large bevel gear 46 is disposed above the inside of the gear housing 8.

The large bevel gear 46 is a hollow structure and is used for connecting a valve transmission mechanism.

The valve transmission mechanism mainly comprises a valve driving shaft sleeve 43, a lifting valve rod nut 11 and a lifting valve rod 42.

The valve driving shaft sleeve 43 is vertically arranged to penetrate through a large bevel gear 46 and is fixed by a large bevel gear and driving shaft sleeve connecting key 45.

A boss on the large bevel gear 46 presses against the upper roller bearing 39 to limit the axial position of the large bevel gear 46 on the drive sleeve 43.

The upper end of the valve driving shaft sleeve 43 penetrates through the gear box body 8, is inserted into an upper rolling bearing seat 44 and is embedded into an upper rolling bearing 39, and the upper rolling bearing seat 44 is fixed on the gear box body 8.

The flange joint surface of the lower end part of the upper rolling bearing seat 44 is provided with a central circular positioning boss, a processing groove is arranged at the corresponding position of the upper rolling bearing seat and matched with the gear box body 8, and the upper rolling bearing seat and the gear box body are connected and fixed through bolts.

The upper rolling bearing seat 44 has a central hole in the upper part, and the lifting valve rod 42 with T-shaped thread on the upper part passes through the central hole and downwards passes through the valve driving shaft sleeve 43 to be matched with the T-shaped thread of the lifting valve rod nut 11, and then is inserted into the valve plate of the rising stem valve body 50 for fixed connection.

A position indication scale protective cover 41 is fixed above the upper central hole of the upper rolling bearing seat 44, and a welding flange arranged at the lower end part of the position indication scale protective cover 41 is inserted into the upper rolling bearing seat 44 for positioning and then is fixed by screws.

The side surface of the position indication scale protective cover 41 is provided with a pointer direction guide opening 59 for moving a vertical pointer, and length scales are processed on two sides of the pointer direction guide opening 59.

The upper end surface of the lifting valve rod 42 is provided with a screw to fix the valve lifting position pointer 40 at a corresponding position, and the corresponding pointer points to the guide port 59.

The lower end of the valve driving shaft sleeve 43 is fixedly sleeved with the lifting valve rod nut 11, a groove is processed in the valve driving shaft sleeve 43, a boss is arranged at the upper end of the lifting valve rod nut 11 and sleeved with the boss to play a role in coaxial positioning, and the valve driving shaft sleeve 43 and the lifting valve rod nut 11 are fixed through the valve rod nut and the transmission shaft sleeve connecting key 16 to play a role in torque transmission.

The lifting valve rod nut 11 is provided with an axial through hole at the center, and an inner boss and T-shaped threads are arranged in the middle and connected with the T-shaped threads on the lifting valve rod 42 in a threaded manner.

An annular boss 60 is processed in the middle of the outer surface of the lifting valve rod nut 11, an upper thrust bearing 15 is arranged on the upper end face of the annular boss 60, a lower thrust bearing 48 is arranged on the lower end face of the annular boss 60 to clamp the annular boss 60 in the middle, the annular boss is then installed in the plug-in valve rod nut rolling bearing seat 14, a bearing gap adjusting and fixing flange 13 (provided with a central through hole) is arranged at the lower end of the lower thrust bearing 48, the lifting valve rod nut 11 can downwards penetrate through the bosses respectively arranged at the upper end and the lower end of the bearing gap adjusting and fixing flange 13, the gap between the upper thrust bearing 15 and the lower thrust bearing 48 can be adjusted to achieve limiting, and the lower end of the lifting valve rod nut 11 is embedded into a lower rolling bearing 12 in the lower rolling bearing seat 10.

The bearing clearance adjusting fixing flange 13 is positioned above the lower rolling bearing seat 10.

The lifting valve rod nut 11 is clamped by the lower rolling bearing seat 10, the lower rolling bearing 12, the bearing clearance adjusting fixing flange 13, the lower thrust bearing 48, the upper thrust bearing 15 and the inserted valve rod nut rolling bearing seat 14 to form a valve rod nut transmission mechanism.

The lifting valve rod nut 11 is vertically arranged, is positioned in the gear box body 8 and penetrates downwards.

The upper portion of the plug-in stem nut roll bearing housing 14, the upper thrust bearing 15 and the annular boss 60 are located below within the gear housing 8.

The lower part of the plug-in valve rod nut rolling bearing seat 14, the bearing clearance adjusting and fixing flange 13, the lower rolling bearing seat 10 and the lower rolling bearing 12 are positioned outside and below the gear box body 8.

The lower part of the plug-in valve rod nut rolling bearing seat 14, the bearing clearance adjusting fixing flange 13 and the lower rolling bearing seat 10 are arranged from top to bottom and fixed at the outer lower part of the gear box body 8 through bolts.

Whereas the conventional design, in which the lower rolling bearing housing 10, the lower rolling bearing 12 and the plug-in stem nut rolling bearing housing 14 are arranged outside the gearbox housing 8, reduces the space taken up on the outside.

The sum of the gravity of the upper and lower rising stem valve plates and the sum of the downward pressure or upward tension and the generated resistance in the lifting process of the valve plates is very large, in the design, the sum is borne by the upper and lower end faces of the annular boss 60 in the middle of the outer part of the lifting valve stem nut 11, namely, the forces are balanced by the lower rolling bearing seat 10, the bearing gap adjusting and fixing flange 13 and the inserted valve stem nut rolling bearing seat 14 in the valve stem nut transmission mechanism, the forces cannot be borne by the large bevel gear 46 and cannot act on the gear box body 8 to deform the gear box body 8, the large bevel gear 46 is arranged above the inner part of the gear box body 8, and the valve stem nut transmission mechanism is inserted into one part of the gear box body 8 so as to reduce the total height of the hydraulic valve and enable the structure to be more compact.

The lower end face of the lower rolling bearing seat 10 is provided with a circle of threaded holes, and the periphery of the central hole is provided with a spigot for positioning, and the spigot is connected with the upper end face of the valve body 50 through a rising stem valve connecting flange 49 in a bolt manner.

The second small bevel gear 17 provided transversely in the gear housing 8 meshes with the large bevel gear 46 placed above. The second small bevel gear 17 has a smaller diameter than the large bevel gear 46.

The shaft root of the second bevel pinion 17 is provided with a boss for pressing the second left gear bearing 38, the second right gear bearing 37 is pressed by the boss at one side of the bearing cover 36, and the bearing cover 36 is fixed at the right side of the gear box body 8 by bolts. The second bevel pinion 17 is a T-shaped shaft, the right side is a thin shaft end, a radial through hole is radially processed at the end part, and a cotter pin 28 is installed. The second bevel pinion 17 shaft is supported in the gear housing 8 by second gear bearings (a second left gear bearing 38 and a second right gear bearing 37).

A left stop piece 35 is fixed on the inner side of the thin shaft end (positioned on the right outer side of the gear box body 8) of the T-shaped shaft of the second bevel pinion 17, and a right stop piece 30 is fixed on the outer side.

The second bevel pinion 17 on the right side of the left stop plate 35 is sleeved with a left bearing 33.

The second bevel pinion 17 on the left side of the right stopper 30 is sleeved with a right bearing 31.

Cotter pin 28 retains right flap 30.

Mounting holes of two side plates of the emergency manual operation handle body 18 with an internal U-shaped space are respectively arranged on the outer ring of the left bearing 33 and the outer ring of the right bearing 31. An emergency hand-operated handle body 18 in the emergency operation device is opened forward and backward.

The emergency operation device includes a left ratchet wheel 71, a left pawl 22, a right ratchet wheel 62, a right pawl 72, a return spring 24, and an emergency manual operation handle body 18.

The left and

right stoppers

35 and 30 restrict axial movement of the left and

right bearings

33 and 31 and the emergency manual operation handle body 18.

The second bevel pinion 17 shaft between the left bearing 33 and the right bearing 31 is provided with a left ratchet wheel 71 and a right ratchet wheel 62 (as long as the ratchet directions are opposite), and gaps are arranged between the left ratchet wheel 71 and the right ratchet wheel 62.

The left ratchet 71 and the right ratchet 62 may be formed to integrally form a double set of ratchet 32.

The double-group ratchet wheel 32 is clamped between two side plates of the emergency manual operation handle 18 and is fixed on the shaft of the second bevel pinion 17 through a ratchet wheel connecting key 26.

The emergency manual operation handle body 18 is rotatable along the second bevel pinion 17 axis through a right bearing 31 and a left bearing 33.

A group of ratchet wheels (a left ratchet wheel 71 and a right ratchet wheel 62) are respectively processed on the left and the right of the double-group ratchet wheel 32, a ratchet wheel groove 73 is arranged between the two groups of ratchet wheels (a gap between the left ratchet wheel 71 and the right ratchet wheel 62), the purpose is to reserve a position for placing a return spring 24 (a torsion spring) between the two pawls, and convenience is brought to the processing of the tooth shape of the ratchet wheels.

The outer end of the emergency manual operation handle body 18 is processed into a cylindrical shape and inserted into the handle sleeve 19, and the emergency manual operation handle body 18 and the handle sleeve 19 are fixed by a fixing pin 20. When a fire disaster happens, the long handle sleeve 19 can be sleeved on the emergency manual operation handle body 18 to close the rising stem valve quickly, so that the emergency manual operation handle body 18 is prevented from being too hot to operate.

The other end of the emergency manual operation handle body 18 needs to be processed inwards in a centering mode, the processing width is the length of the double groups of ratchet wheels 32, the processing depth depends on the distance needed by the movement of a ratchet mechanism formed by the two pawls and the double groups of ratchet wheels 32, the bottom of the emergency manual operation handle body 18 is processed into the shape of the root of the corresponding pawl, the depth is suitable for the normal and flexible work of the corresponding pawl, the two pawls are placed and processed left and right, a spacing groove 64 is formed between the two pawls to separate the two pawls, and the position of the spacing groove 64, which corresponds to the hole of the middle stopper 34, can be used for placing the reset spring 24 and limiting the two pawls to swing greatly.

The emergency manual operation handle body 18 is provided with a left pawl slot 75 corresponding to the root of the left pawl 22.

The emergency manual operation handle body 18 is provided with a right pawl groove 74 corresponding to the root of the right pawl 72.

The horizontal pawl and the return spring fixing pin 23 are fixedly arranged on the emergency manual operation handle body 18 in a penetrating way and are locked by a flat pad and a cotter pin.

The left pawl elastic sleeve 61 (cylindrical rubber plastic elastic sleeve) is sleeved on the pawl and reset spring fixing pin 23, and the root of the left pawl 22 is provided with a shaft hole sleeved on the left pawl elastic sleeve 61.

The right pawl elastic sleeve 21 (cylindrical rubber plastic elastic sleeve) is sleeved on the pawl and reset spring fixing pin 23, and the root of the right pawl 72 is provided with a shaft hole sleeved on the right pawl elastic sleeve 21.

The middle stop block 34 is sleeved outside the return spring 24, and the middle stop block 34 corresponds to the spacing groove 64 and is fixed in the emergency manual operation handle body 18 through a bolt.

One end of a return spring 24 extends out along the position between the middle stop block 34 and the left pawl 22 and is clamped at the groove of the left pawl handle 65, the other end of the return spring 24 extends out along the position between the middle stop block 34 and the right pawl 72 and is clamped at the groove of the right pawl handle 66, the two pawls are close to the axial direction of the second bevel pinion 17 by the inward spring force, the heads of the two pawls are always contacted and attached to the corresponding double groups of ratchet wheels 32, namely the left pawl 22 corresponds to the left ratchet wheel 71, and the right pawl 72 corresponds to the right ratchet wheel 62.

The pawl and return spring fixing pin 23 passes through the two pawls, the two elastic sleeves, the return spring 24 and the middle stopper 34 together, and fixes the pawls, the two elastic sleeves, the return spring 24 and the middle stopper in the emergency manual operation handle 18.

The left pawl 22 is provided with a left pawl pin hole 68 corresponding to a first through hole 70 formed in a right side plate of the emergency manual operation handle body 18, and the left pawl pin hole 68 and the first through hole 70 are configured such that the left pawl clutch pin 63 is inserted and fixed between the left pawl pin hole 68 and the first through hole 70 when the left pawl 22 is outwardly bent to disengage the left pawl 22 from the left ratchet wheel 71. The left pawl clutch latch 63 can be connected to the emergency manual handle 18 by a corresponding chain and will not be lost after being pulled out.

The right pawl 72 is provided with a right pawl pin hole 69 corresponding to the second through hole 67 formed in the right side plate of the emergency manual operation handle body 18, and the right pawl pin hole 69 and the second through hole 67 are arranged such that the right pawl clutch pin 25 is inserted and fixed between the right pawl pin hole 69 and the second through hole 67 when the right pawl 72 is pulled outward to disengage the right pawl 72 from the right ratchet 62. The right pawl clutch latch 25 is connectable to the emergency manual handle 18 by a corresponding chain and is not lost after being pulled out.

In fig. 3, the first through hole 70 and the second through hole 67 are overlapped in the back and front positions, the left pawl clutch bolt 63 and the right pawl clutch bolt 25 are overlapped in the back and front positions, and the actual space positions are staggered in the back and front positions and different in length. The corresponding long clutch bolt can also be positioned more stably by arranging a positioning hole on the left side plate.

The two elastic sleeves are used for moving the emergency manual operation handle 18 when the corresponding side pawl ratchet mechanism works, for example, the left pawl 22 is enabled to clamp the ratchet of the left ratchet wheel 71, the head of the left pawl 22 is forced to move in the opposite direction, the left pawl elastic sleeve 61 is compressed, the left pawl 22 is enabled to move to enable the tail of the left pawl 22 to be in contact with the left pawl groove 75, namely, the emergency manual operation handle 18, the original force bearing point is changed into the stress of the emergency manual operation handle 18, the pawl is prevented from being forced to deform the return spring fixing pin 23, on the other hand, the pawl is prevented from swinging due to overlarge gaps between the pawl and the return spring fixing pin 23, and the phenomenon of uneven stress is avoided. The two groups of pawl ratchet mechanisms are manually operated respectively, so that the second bevel gear 17 can rotate clockwise or anticlockwise, the lifting valve rod 42 is lifted or lowered by matching with the thread direction of the lifting valve rod 42, the open and close of the rising stem valve are realized, and the aim of opening or closing the emergent manual operation valve can be realized.

When the manual operation pawl ratchet mechanism works, the reset spring 24 enables the pawl to be rotated to be pressed by the reset spring 24 to be attached to a corresponding ratchet wheel by pulling out the clutch bolt of one pawl, so that the second bevel pinion 17 can only rotate towards one direction, when the pawl needs to rotate towards the other direction, the clutch bolt of the other side is pulled out, the clutch bolt of the unused side is inserted to enable the unused pawl to be separated from the corresponding ratchet wheel, the emergency manual operation handle 18 is shaken, and the second bevel pinion 17 rotates towards the other direction to drive the lifting valve rod 42.

The encoder 27 is arranged for monitoring and detecting the operation state of the valve, the shaft end (wired or wireless) of the encoder 27 is inserted into the shaft end central hole of the second bevel pinion 17 and fixed, the mounting flange at the front part of the encoder 27 is connected with one end of the encoder bracket 29, and the other end of the encoder bracket 29 is fixed on the right gear box body 8 by screws.

The rising stem valve is a valve to be opened and closed and is a known valve, and the drift diameter is 500mm-2 m.

The working principle is as follows:

normally, the hydraulic system normally operates in an electrical state.

The hydraulic ball valve 2 is in the closed state.

The left pawl 22 and the right pawl 72 are opened and fixed by the left pawl clutch bolt 63 and the right pawl clutch bolt 25 respectively, and the two pawls are opened without influencing the rotation of the second small bevel gear 17 shaft and the two ratchet wheels thereon along with the large bevel gear 46.

When the hydraulic control system receives an electric signal, the hydraulic system is started, pressure oil enters an A cavity or a B cavity of the hydraulic motor, the hydraulic motor rotates, torque and rotating speed are transmitted to the first small bevel gear 9 through the coupler 5 and drive the large bevel gear 46 to move, the large bevel gear 46 rotates for one circle and the first small bevel gear 9 rotates for multiple circles due to the ratio of the large bevel gear to the small bevel gear, a speed reduction booster is formed, the output torque is amplified and then transmitted to the lifting valve rod nut 11 through the valve driving shaft sleeve 43 arranged in the central hole of the large bevel gear 46, the lifting valve rod nut 11 rotates and then transmits the torque to the lifting valve rod 42 to drive the valve plate of the lower open rod valve to move up and down, and the valve rod of the open rod valve needs to move up and down, and the valve driving shaft sleeve 43 is specially designed into a through core type structure with the center capable of penetrating through the valve rod.

The large bevel gear 46 drives the valve driving shaft sleeve 43 and the lifting valve rod nut 11 to synchronously rotate.

The lifting valve rod 42 sleeved in the lifting valve rod nut 11 is in threaded fit with the lifting valve rod nut 11. The lift valve stem 42 moves up and down and the valve lift position pointer 40 moves up and down in the pointer-pointing guide port 59.

In order to bear the axial force generated by driving the valve, a plug-in type valve stem nut transmission mechanism is designed, two thrust roller bearings (an upper thrust bearing 15 and a lower thrust bearing 48) are oppositely arranged on the lifting valve stem nut 11, so that the axial force generated when the valve is driven and the frictional resistance generated if the thrust bearing is not arranged are effectively borne, and the multi-turn valve can reliably work for a long time.

When power is off, the hydraulic ball valve 2 is opened manually.

The working oil inlet/outlet A, B can be switched on and off through the hydraulic ball valve 2, and the hydraulic ball valve 2 is in a closed state under normal conditions (in an electric condition). When power failure happens accidentally, the valve needs to be closed or opened, the manual hydraulic ball valve 2 can be opened firstly, the working oil inlet and outlet A and B are communicated through the hydraulic ball valve 2, the hydraulic motor 1 is decompressed to release self-locking, when the manual emergency manual operation handle 18 is moved, the second small bevel gear 17 can be easily driven to rotate, the large bevel gear 46, the valve driving shaft sleeve 43 and the lifting valve rod nut 11 are driven to rotate, the lifting valve rod 42 is driven to move up and down, and meanwhile, the first small bevel gear 9 is unloaded to rotate.

Thereby realizing the purpose of manually opening and closing the valve. The leakage oil generated when the hydraulic motor 1 works can be discharged back to the hydraulic control system from the oil drainage port L on the shell or the end cover.

The power for opening and closing the multi-turn hydraulic valve is provided by a hydraulic control system, the hydraulic control system comprises a hydraulic oil pump, a motor, a hydraulic original device, an oil tank, a pipeline and the like, and the multi-turn hydraulic valve is a known technology. When the valve is opened, the load is large, and a constant-power variable pump in the hydraulic control system can automatically output pressure meeting the load requirement according to the load requirement. When a valve plate in the valve rises to an upper dead point, the system pressure can be increased, the pressure relay and the encoder 27 arranged on the valve can send signals to control the reversing valve to act to cut off an oil way or enable the hydraulic system to lose pressure to brake the hydraulic motor 1, and because the safety overflow valve is arranged in the hydraulic control system, when the system pressure reaches the upper dead point and the lower dead point, the system pressure gradually rises to a set value of the safety overflow valve, the safety overflow valve works, the system pressure is maintained at a set safety pressure value, and thus the valve cannot be damaged. The load is small at the beginning stage of valve closing, the hydraulic oil pump can automatically realize low-pressure large-flow oil supply according to the load, the valve plate can rapidly descend, before the valve plate moves to a bottom dead center, the resistance load can be gradually increased, the hydraulic oil pump can automatically realize high-pressure small-flow output according to the actual condition of the load, the valve plate can slowly descend, when the pressure is increased to a pressure value set by the safety valve, the valve cannot be impacted after the system is balanced, when the bottom dead center is reached, the encoder 27 and the pressure relay (pressure sensor) can simultaneously send out signals, the oil circuit is cut off or the oil circuit system is depressurized to brake the hydraulic motor 1, at the moment, the hydraulic motor 1 brakes, and the valve rod nut transmission mechanism is also in a braking state to enable the lifting valve rod 42 to realize self-locking.

The multi-rotation type hydraulic valve has the advantages that the starting torque is large, the output torque and the rotating speed can change according to the load change during the operation, the wireless monitoring and the control of the opening and the closing of the multi-rotation type hydraulic valve can be realized, the operation of the multi-rotation type hydraulic valve is more advanced, reliable, safe, long in service life, high in automatic control precision and control degree, and the manual operation can be realized in an emergency state.

The multi-rotation type hydraulic valve driven and controlled by the hydraulic motor 1 has the advantages of large starting torque, safety and reliability in valve operation, the encoder 27 on the hydraulic valve can accurately and automatically detect and feed back the opening and closing position and state of the valve, the hydraulic system can automatically detect the load change in the valve operation process, the output torque and the rotating speed of the hydraulic motor 1 can be automatically adjusted, and the flexible control of the opening and closing of the valve and the impact and vibration of the inertia force on the valve can be realized. After the encoder 27 is adopted, the operation of the hydraulic valve can be remotely and wirelessly monitored and controlled, and the automation and the intellectualization of the valve are realized. In addition, the risk can be effectively avoided by arranging the hydraulic system in a remote way to control the hydraulic valve, and the application field can be expanded to occasions with high pollution, flammability, explosiveness, petroleum and natural gas storage and delivery and the like. The multi-rotation type hydraulic valve also has the dual self-locking functions of hydraulic motor self-locking and mechanical self-locking, so that the opening degree of the valve is controlled more accurately, and the valve also has the emergency manual opening and closing function. The valve is safer and more reliable to operate.

Example 2

Embodiment 2 is substantially the same as embodiment 1 except that the rising stem valve is replaced with a non-rising stem valve, and a non-rising stem valve driving valve stem (upper solid stem) 53 is not moved up and down but rotated.

The lift valve stem 42, the valve driving boss 43 and the lift valve stem nut 11 in embodiment 1 are replaced with a blind valve driving valve stem 53.

The upper end of the vertically arranged non-rising stem valve driving valve rod 53 is fixedly connected with the inner hole of the large bevel gear 46 by a non-rising stem valve driving valve rod connecting key 76.

The lower end of the non-rising stem valve driving valve rod 53 is provided with a lower valve rod rolling bearing, and the lower valve rod rolling bearing is fixedly supported on the inner side of the gear box body 8 through a lower valve rod rolling bearing seat 54.

The lower part of the valve rod lower rolling bearing seat 54 extends out of the edge of the gear box body 8 and is fixed.

The upper end of the non-rising stem valve driving valve rod 53 is provided with a valve rod upper rolling bearing, and the non-rising stem valve driving valve rod is fixedly supported on the outer side above the gear box body 8 through a valve rod upper rolling bearing seat 56.

In addition, the shaft end of the encoder 27 is inserted into the central hole on the upper end surface of the non-rising stem valve driving valve rod 53 and fixed, and the mounting flange at the front part of the encoder 27 is fixed on a rolling bearing seat 56 on the valve rod.

The emergency operation device (emergency manual operation handle body 18 and the structure at the double set ratchet wheel 32) in embodiment 1 is replaced by the manual emergency dial 57 fixed on the right outside of the gear housing 8 on the second bevel pinion 17 shaft by the flat key 58 because of the space.

Instead of the emergency manual operating handle 18 and the two ratchet-pawl mechanisms, a manual emergency dial 57 may be used to manually open and close the valve if space permits in embodiment 1.

The non-rising stem valve driving valve rod 53 is fixedly connected with the non-rising stem valve rod 52 at the lower part.

The power output of the speed reduction booster (large bevel gear 46) is connected with the power input of the valve transmission mechanism (the hidden rod valve drives the valve rod 53).

A bearing adjustment shim 55 is provided below the stem lower rolling bearing support 54.

The non-rising stem valve is a valve to be opened and closed and is a known valve, and the drift diameter is 500mm-2 m.

The lower end of the non-rising stem valve stem 52 is connected with a nut fixed on a non-rising stem valve plate through threads, and a vertical movement guide device is arranged between the non-rising stem valve stem 52 and the nut, so that the valve plate of the non-rising stem valve can be opened up and down.

The lower stem rolling bearing support 54 is fixedly connected to the blank stem valve body 51.

The invention can realize safe and reliable opening and closing of the valve (open rod valve or hidden rod valve), can realize flexible control on the whole opening or closing process of the valve, reduces the impact and vibration on the valve generated in the operation process of the driving device, and can realize effective self-locking of the valve core (valve plate). The invention can also realize the functions of remote wireless control and monitoring of the hydraulic valve, can set and display the opening and closing states of the valve, and can implement manual operation of emergency situations.

Claims

1. A multi-rotation hydraulic valve comprises a hydraulic motor (1) and a deceleration booster, and is characterized in that:

the speed reduction booster comprises a first small bevel gear (9) and a large bevel gear (46) which are meshed with each other;

the diameter of the first small bevel gear (9) is smaller than that of the large bevel gear (46);

the output shaft of the hydraulic motor (1) which is transversely arranged is fixedly connected with a first bevel pinion (9) shaft which is transversely arranged;

a first bevel pinion (9) shaft is supported in the gear box body (8) through a first gear bearing;

the large bevel gear (46) is arranged above the inner part of the gear box body (8);

the large bevel gear (46) is connected with a power input part of the valve transmission mechanism;

the power input part of the valve transmission mechanism is a vertically arranged valve driving shaft sleeve (43) which is fixedly connected with a large bevel gear (46);

the valve transmission mechanism comprises a valve driving shaft sleeve (43), a lifting valve rod nut (11) and a lifting valve rod (42);

the upper end of the valve driving shaft sleeve (43) penetrates through the gear box body (8) and is inserted into an upper rolling bearing (39) embedded in an upper rolling bearing seat (44), and the upper rolling bearing seat (44) is fixed on the gear box body (8);

the lifting valve rod (42) penetrates through the upper rolling bearing seat (44) and downwards penetrates through the valve driving shaft sleeve (43) to be in threaded fit with the lifting valve rod nut (11);

a position indication scale protective cover (41) is fixed above the upper rolling bearing seat (44);

the side surface of the position indication scale protective cover (41) is provided with a pointer pointing guide port (59), and length scales are arranged on two sides of the position indication scale protective cover;

a valve lifting position pointer (40) is fixed on the upper end surface of the lifting valve rod (42), and the corresponding pointer points to the guide port (59);

the lower end of the valve driving shaft sleeve (43) is fixed with the lifting valve rod nut (11);

an annular boss (60) is arranged in the middle of the outer surface of the lifting valve rod nut (11), an upper thrust bearing (15) is arranged on the upper end face of the annular boss, a lower thrust bearing (48) is arranged on the lower end face of the annular boss, the annular boss is arranged in an inserted valve rod nut rolling bearing seat (14), a bearing clearance adjusting and fixing flange (13) is arranged at the lower end part of the lower thrust bearing (48), and the lower end of the lifting valve rod nut (11) is embedded into a lower rolling bearing (12) in a lower rolling bearing seat (10);

the inserted valve rod nut rolling bearing seat (14), the bearing clearance adjusting fixing flange (13) and the lower rolling bearing seat (10) are fixedly connected with the gear box body (8);

the upper part of the plug-in valve rod nut rolling bearing seat (14), the upper thrust bearing (15) and the annular boss (60) are positioned below the gear box body (8);

the lower part of the plug-in type valve rod nut rolling bearing seat (14), the bearing clearance adjusting and fixing flange (13), the lower rolling bearing seat (10) and the lower rolling bearing (12) are positioned below the outside of the gear box body (8);

the big bevel gear (46) placed above is meshed with a second small bevel gear (17) transversely arranged in the gear box body (8); the diameter of the second small bevel gear (17) is smaller than that of the large bevel gear (46);

a second bevel pinion (17) shaft is supported on the right side in the gear box body (8) through a second gear bearing;

the right end of the shaft of the second bevel pinion (17) is provided with an emergency operation device and an encoder (27);

the emergency operation device is positioned on the right outer side of the gearbox body (8);

a left bearing (33) and a right bearing (31) are arranged on the part of the second bevel pinion (17) positioned on the right outer side of the gear box body (8);

mounting holes of two side plates of an emergency manual operation handle body (18) with an internal U-shaped space are respectively arranged on the outer ring of a left bearing (33) and the outer ring of a right bearing (31);

a left ratchet wheel (71) and a right ratchet wheel (62) with opposite ratchet directions are fixed on a second bevel pinion (17) shaft between the left bearing (33) and the right bearing (31);

the transversely arranged pawl and reset spring fixing pin (23) is fixedly arranged on the emergency manual operation handle body (18) in a penetrating way, and is sleeved with a left pawl (22) and a right pawl (72), and a reset spring (24) is sleeved between the left pawl and the right pawl;

one end of a return spring (24) is clamped at the groove of the left pawl handle (65), the other end of the return spring (24) is clamped at the groove of the right pawl handle (66), and the return spring (24) is set to have a spring force inwards so that the left pawl (22) and the right pawl (72) are close to the axis direction of the second bevel pinion (17);

a left pawl pin hole (68) is formed in the left pawl (22) and corresponds to a first through hole (70) of the emergency manual operation handle body (18), and the left pawl pin hole (68) and the first through hole (70) are arranged in a way that a left pawl clutch bolt (63) is inserted between the left pawl pin hole (68) and the first through hole (70) for fixation when the left pawl (22) is broken outwards to separate the left pawl (22) from a left ratchet wheel (71);

a right pawl pin hole (69) is formed in the right pawl (72) and corresponds to a second through hole (67) of the emergency manual operation handle body (18), and the right pawl pin hole (69) and the second through hole (67) are arranged in a way that when the right pawl (72) is broken off outwards, and the right pawl (72) is separated from the right ratchet wheel (62), a right pawl clutch bolt (25) is inserted between the right pawl pin hole (69) and the second through hole (67) for fixation.

2. A multi-turn hydraulic valve according to claim 1, wherein:

the emergency manual operation handle body (18) is provided with a left pawl groove (75) corresponding to the root part of the left pawl (22);

the emergency manual operation handle body (18) is provided with a right pawl groove (74) corresponding to the root part of the right pawl (72);

a left pawl elastic sleeve (61) is arranged between the left pawl (22) and the pawl and return spring fixing pin (23);

and a right pawl elastic sleeve (21) is arranged between the right pawl (72) and the pawl and return spring fixing pin (23).