CN116464631A - Large-size reciprocating pump valve with multistage buffering function - Google Patents

Abstract

The invention discloses a large-size reciprocating pump valve with a multistage buffering function, which comprises a pressure cap, a spring seat, a conical compression spring and a valve seat which are sequentially connected, wherein an axially movable valve core is sleeved in an inner hole of the valve seat, the valve core is connected with the valve seat through a multistage buffering piece, and the multistage buffering piece comprises: and the bottom buffer piece, the side buffer piece and the top buffer piece are coaxially and sequentially arranged with the valve core. Gaps are reserved at the connection or embedding positions of the bottom buffer piece and the side buffer piece and the valve seat, the gaps gradually decrease from one end close to the spring seat to a far away section, and the buffer pieces of all stages are buffered in sequence due to different contact sequences in the buffering process. The multistage buffering component realizes the multistage buffering function of the reciprocating pump by arranging the multistage buffering components, and particularly comprises the bottom buffering component, the side buffering component and the top buffering component.

Description

Large-size reciprocating pump valve with multistage buffering function

Technical Field

The invention discloses a large-size reciprocating pump valve with a multistage buffering function, and relates to the technical field of reciprocating pump valve core buffering devices.

Background

With the increase of deep wells and ultra-deep wells, the formation pressure is increased, and complex well structures such as horizontal wells and the like appear, the power and the discharge capacity of the oil gas drilling and production reciprocating pump are increasingly larger, and the large-size valve core and the matching of the inner hole of the valve seat and the outer cylindrical surface of the claw-shaped part at the lower part of the valve core are required to be adopted to ensure that the guiding part of the valve core has good guiding effect.

When the pump valve is installed in the reciprocating pump valve box, the compression spring is installed on the upper part of the valve core, so that the valve disc and the valve seat sealing conical surface of the valve core are subjected to certain pressure when the pump valve works. However, when the valve core falls back, under the action of pressure difference between the upper and lower sides of the valve core, spring force and inertia force of the valve core, larger impact force can be generated on the conical surfaces of the valve disc and the valve seat, so that grooves appear on the conical surfaces of the valve disc and the valve seat, and even damage such as damage to valve rubber is caused. The larger the valve disc size, the more impact, and particularly for higher stroke reciprocating pumps, the higher the risk of failure of the pump valve.

The technology for reducing the impact force of the reciprocating pump valve in the prior art comprises the methods of fixedly connecting a piston at the lower part of a valve body, arranging vibration damping rubber between a valve rod and a valve disc, adding a buffer cushion on the bottom surface of a valve core and the upper surface of a valve seat rib and the like. These techniques only achieve a single shock absorption and use of rubber cushioning can only absorb small impact forces. The rubber cushion has a short life in high-speed or higher temperature fluids, especially when the cushion or cushion rubber is the only damping means in a single shock absorber.

Therefore, how to realize the function of multistage shock absorption to improve the service life of the pump valve of the reciprocating pump is a problem to be solved.

Summary of the invention

The invention aims to provide a large-size reciprocating pump valve with a multistage buffering function, which realizes the multistage buffering function aiming at valve core impact in a reciprocating pump.

In order to achieve the technical purpose and the technical effect, the invention is realized by the following technical scheme:

a large-sized reciprocating pump valve with a multistage buffering function, comprising: the valve seat is characterized by comprising a pressing cap, a spring seat, a conical compression spring and a valve seat which are sequentially connected, wherein a valve seat inner hole is formed in the center of the valve seat, a valve core capable of axially moving is sleeved in the valve seat inner hole, and a multi-stage buffer piece is arranged between the valve core and the valve seat.

Further, the multi-stage buffer includes: the bottom buffer piece, the side buffer piece and the top buffer piece are coaxially and sequentially arranged with the movement of the valve core, the bottom buffer piece is arranged on a plane where the valve seat reaches corresponding to the limit of the falling-back progress of the valve core, the side buffer piece is at least one, the side buffer piece extends out and is not axial extension, extension with the gomphosis of disk seat hole, top buffer piece both ends fixed connection spring holder and case.

Furthermore, gaps are reserved at the connection or embedding positions of the bottom buffer piece and the side buffer piece and the valve seat, the gaps gradually decrease from one end close to the spring seat to a far section, and the buffer pieces of all stages are buffered in sequence due to different contact sequences in the buffering process.

Further, the gap between each adjacent cushioning member is reduced by a value of 1-2mm.

Further, the side buffer member is one, one side of the side buffer member is attached to the tail end of the valve seat near the spring seat section, the other side of the side buffer member is an extending part integrally connected to the valve core, the extending part and the tail end of the valve seat form an embedded structure, and the inclination angle of an attaching surface between the side buffer member and the tail end of the valve seat relative to a horizontal plane is 30-45 degrees.

Further, the buffer piece is a rubber ring, and the contact surface of the rubber ring and the valve core protrudes 1-2mm more than the sealing conical surface of the valve core.

Further, the valve core is a claw-shaped valve core, the claw-shaped end of the claw-shaped valve core gradually approaches the bearing disc in the falling process of the valve core, the claw-shaped end of the valve core contacts with the bearing disc when the pump valve is completely closed, the inner diameter of the bottom buffer piece is 5-6mm larger than that of the bearing disc, the outer cylinder diameter of the bearing disc is 8-10mm larger than that of the inner hole of the valve seat and is in clearance fit with the valve seat, and the bearing disc moves up and down freely in a clearance space during buffering.

Further, the bottom cushioning member is a wave spring, the wave spring comprises different models, and the stiffness of the wave spring is proportional to the diameter of the corresponding pump valve.

Further, in a static state, a gap between the side buffer piece and the valve seat is 1mm, and the bottom buffer piece is in direct contact with the valve core, namely, the bearing disc is in direct contact with the wave spring.

The beneficial effects are that:

the multistage buffering component realizes the multistage buffering function of the pump valve of the reciprocating pump by arranging the multistage buffering component, and particularly comprises the bottom buffering component, the side buffering component and the top buffering component. In addition, compared with the buffer device in the prior art, the multistage buffer structure can only be suitable for a straight rod type valve core, and the multistage buffer structure can be suitable for a valve core with a claw type structure.

Finally, in some preferred cases, good cushioning can be achieved by using different wave springs.

Of course, it is not necessary for any one product to practice the invention to achieve all of the advantages set forth above at the same time.

Drawings

FIG. 1 is a schematic diagram of a pump valve of a large-sized reciprocating pump with a multi-stage buffering function according to an embodiment of the present invention;

FIG. 2 is a schematic view of a side bumper according to an embodiment of the present invention;

FIG. 3 is a schematic view illustrating an inclination angle of a side buffer according to an embodiment of the present invention;

FIG. 4 is a schematic view of a bottom bumper installation according to an embodiment of the present invention;

fig. 5 is a three-dimensional schematic view of a bearing disc structure according to an embodiment of the present invention;

FIG. 6 is a schematic view of a three-dimensional structure of a wave spring according to an embodiment of the present invention;

FIG. 7 is a schematic view showing a three-dimensional structure of a fixing screw sleeve according to a preferred embodiment of the present invention;

FIG. 8 is a schematic view of a valve seat according to a preferred embodiment of the present invention;

FIG. 9 is a three-dimensional schematic view of a claw-shaped valve core and rubber assembly structure according to a preferred embodiment of the invention;

FIG. 10 is a diagram showing different operating states of the tertiary buffer according to the preferred embodiment of the present invention;

in the accompanying drawings:

1-cap pressing; 2-spring seat/top bumper; 3-conical compression springs; 4-claw spool/spool; 5-rubber ring/side cushioning; 6-valve seat; 7-wave spring/bottom bumper; 8-fixing the screw sleeve; 9-a bearing plate;

Detailed Description

In order to more clearly describe the technical scheme of the embodiment of the present invention, the embodiment of the present invention will be described in detail below with reference to the accompanying drawings.

Example 1

The reciprocating pump is a common industrial pump, and the working principle is as follows: when the suction valve of the pump body is opened, the piston in the pump body is retracted, thereby generating negative pressure, and the medium (usually liquid) in the pump body is introduced into the pump body through the suction valve. With the suction valve of the pump body closed, the piston within the pump body is pushed forward, compressing the medium, causing it to be expelled through the discharge valve. Reciprocating pumps are usually provided with a suction valve and a discharge valve, which serve to control the direction of flow of the medium during operation of the pump. Reciprocating pumps typically require an external power source (e.g., motor, engine, etc.) to drive the reciprocating motion of the pistons, thereby completing the pump operation.

The reciprocation of the spool 4 can be understood with reference to (a) (b) in fig. 10. In the valve core opening process, the length of the conical compression spring is shortened, and the length of the conical compression spring is longest in the closing state.

The device in the embodiment also comprises a main structure of the reciprocating pump in the prior art, wherein the main structure also comprises a pressure cap 1, a spring seat 2, a conical compression spring 3 and a valve seat 6 which are sequentially connected, an inner hole of the valve seat 6 is formed in the center of the valve seat 6, a valve core 4 capable of axially moving is sleeved in the inner hole of the valve seat 6, and a multi-stage buffer piece is arranged between the valve core 4 and the valve seat 6.

The foregoing structural features are applicable to all reciprocating pumps. I.e. these features are applicable not only to standard reciprocating pumps, but also to other types of reciprocating pumps, such as diaphragm pumps, plunger pumps, etc.

The applicant combines the pump valve structure of the existing reciprocating pump, and comprehensively considers that when the pump valve is in reciprocating pump operation, when the valve core 4 falls back, larger impact force can be generated on the conical surfaces of the valve disc and the valve seat 6, and the impact force is caused by the combined action of the up-and-down pressure difference of the valve core 4, the spring force and the inertia force of the valve core 4. However, the conventional buffer device can buffer the impact force for a single time, but the buffer effect is poor and the service life of the buffer structure is not long.

The multistage buffering member in the pump valve of the large-sized reciprocating pump having the multistage buffering function according to the present embodiment therefore includes: the valve seat 4 is characterized in that the valve seat 4 is provided with a bottom buffer piece 7, a side buffer piece 5 and a top buffer piece 2 which are coaxially and sequentially arranged in a moving way, the bottom buffer piece 7 is arranged on a plane where the valve seat 6 reaches the limit of the falling process of the valve seat 4, at least one side buffer piece 5 extends out of a non-axial extension part, the extension part is embedded with an inner hole of the valve seat 6, and two ends of the top buffer piece 2 are fixedly connected with the spring seat 2 and the valve seat 4.

The bottom buffer 7 is a part mounted on the valve seat 6, corresponding to the fall limit reaching plane of the valve spool 4. In this embodiment, a certain structural design and material selection are possible.

For example, in some embodiments, different shapes, sizes, and positions of the cushioning members, such as cylindrical, conical, annular, etc., may be employed to accommodate different pump valve configurations and operating conditions. Materials with good cushioning properties and wear resistance, such as rubber, polyurethane, metal springs, etc., may be selected. These materials can absorb and disperse the impact force during the falling back of the valve element 4, thereby reducing the impact effect on the same conical surface of the valve disc and the valve seat 6.

In one embodiment, the bottom buffer 7 may be of a conical design, and the material is polyurethane, through its excellent elasticity and wear resistance, which can effectively absorb and disperse impact forces during the fall back of the valve core 4.

The impact force generated when the valve core 4 falls back can be absorbed and dispersed, so that impact influence on the conical surfaces of the valve disc and the valve seat 6 is reduced. The bottom buffer 7 protects the normal operation of the valve core 4 and the valve seat 6 by buffering the falling back of the valve core 4 during the operation of the reciprocating pump.

The side bumper 5 may comprise a plurality of extensions having a non-axial direction. This extension is normally engaged with the bore of the valve seat 6 to form a cushioning structure. The side buffer 5 is able to buffer the movement of the valve core 4 by cooperating with the bottom buffer 7, thereby reducing the impact force generated by the valve core 4 during operation. This design helps prevent the impact force of the valve element 4 from falling back from damaging the conical surfaces of the valve disc and valve seat 6.

In a specific embodiment, the side buffer member 5 may be of annular design, and made of rubber, and forms a buffer structure by its good buffer performance and the engagement with the inner hole of the valve seat 6, so as to buffer the movement of the valve core 4.

The top buffer piece 2 is positioned at two ends between the spring seat 2 and the valve core 4 and is fixedly connected with the two ends. In some embodiments, a connecting spring is used, high-strength stainless steel is selected as a material, and the movement of the valve core 4 is buffered and supported through the elastic characteristic of the connecting spring, so that a multi-stage buffering function is realized.

The top buffer part 2 can buffer the upward movement of the valve core 4 in the opening working process, reduce the impact force of the valve core 4 on the press cap 1, simultaneously provide an initial power for the valve core 4 when the valve core 4 starts to move downwards, accelerate the valve core 4 to start to close and reduce the closing lag angle of the valve core 4.

The bottom cushion member 7 and the side cushion member 5 in the foregoing embodiments are designed to cushion the impact force generated by the falling back of the valve element 4 in the operation of the reciprocating pump in multiple stages by the synergistic effect, thereby reducing the influence of the impact force on the conical surfaces of the valve disc and the valve seat 6 and improving the cushioning effect and the life of the cushioning structure. The design of the multistage buffering function is suitable for a large-size reciprocating pump, and the performance and reliability of the reciprocating pump can be improved.

The applicant needs to consider the impact process caused by the fall back when designing the multi-stage buffer structure. Therefore, it is necessary to ensure that each bumper is fully functional at the time of design. However, in the previous embodiment, all of the cushioning members, if in direct contact with the valve seat 6, would result in the multi-stage cushioning members acting simultaneously, essentially equivalent to the action of a single cushioning member. In this case, the cushioning effect cannot be improved. To solve this problem, the applicant considered to adopt a buffer structure in which a certain space is reserved to achieve sequential contact, so as to ensure that each buffer member fully functions, thereby achieving a better buffer effect.

In other words, such a gap design may ensure that during the fall back of the spool 4, the bottom bumper 7 first contacts and dampens the impact force, then the side bumpers 5 contact and continue to cushion the impact force, and finally the top bumpers 2 contact and complete the cushioning effect. The buffer sequence can avoid the buffer parts contacting at the same time, so that the mutual interference among the buffer parts is reduced, and the progressive buffer effect is ensured.

The design of such a gap may also allow for some displacement and deformation during cushioning, thereby providing better cushioning performance. With the increase of the falling speed of the valve core 4, the gap between the buffer parts is gradually reduced, so that the impact force and the acting time can be controlled more accurately, and a better buffer effect is achieved.

In consideration, the gap design should be determined according to practical application requirements and design requirements, and factors including the mass of the valve element 4, the falling speed, the characteristics of the pump medium and the like need to be taken into consideration. In practical engineering application, the multistage buffering structure can be optimized by adjusting parameters such as the size, the shape, the size of a gap and the like of the buffering piece so as to meet buffering requirements under different working conditions.

Thus, in some embodiments, considering that the lift of the pump valve of the reciprocating pump is between 10 and 20mm, a gap of 1 to 2mm may be applied to the pump valve of the large size of the present design, and the relative difference in the relative contact surface distance between the side buffers 5 should also be within the aforementioned range. When the gap is too large, the bottom buffer piece 7 needs to generate larger compression deformation to enable the side buffer piece 5 to be in contact with the valve seat 6, and the conical surface of the valve core 4 is possibly not in contact with the conical hole surface of the valve seat 6 when the bottom buffer piece 7 reaches the compression limit, so that the pump valve is not tightly closed. This gap is too small, and may cause the bottom cushion 7 to come into contact with the side cushion 5 at almost the same time due to a processing error, reducing the cushioning effect of the bottom cushion 7.

For the purpose of illustrating in detail the principles of the present embodiment invention, applicant makes specific description in connection with the preferred embodiments described below.

In this preferred embodiment, the side buffer member 5 is one, one side of the side buffer member 5 is attached to the end of the valve seat 6 near the spring seat 2, and the other side is an extension integrally connected to the valve core 4, and the extension and the end of the valve seat 6 form a jogged structure, and the structure can be understood with reference to fig. 2.

The present preferred embodiment has the advantage that it can achieve the purpose of efficient buffering and precise control of the buffering effect by optimizing the shape, size, material and other parameters of the buffering member with a simple fitting structure in combination with the foregoing structure. And because the side buffer piece 5 and the valve core 4 are integrally connected (see fig. 9), the buffer piece cannot be loosened or fall off, and therefore the reliability and stability of the whole buffer system are improved. At the same time, the jogged structure can reduce the relative movement between the buffer parts and reduce the risks of abrasion and faults.

To perfect the structure of this preferred embodiment, the bottom buffer 7 and the top buffer 2 are arranged according to a standard axial direction, which is a simplified block diagram with reference to fig. 2. Specifically, the contact surface between the side damper 5 and the tip end of the valve seat 6 is inclined at an angle of 30 ° to 45 ° with respect to the horizontal.

The bottom cushion 7 and the side cushion 5 are stressed as follows in connection with fig. 4: when the claw-shaped end of the valve core 4 is not contacted with the bearing disc 9, the wave spring 7 has a certain precompression to generate an upward thrust to the bearing disc 9, so that the upper end of the bearing disc 9 is contacted with a positioning step at the bottom of the valve seat 6 (figure 4 a); when the claw-shaped end of the valve core 4 contacts with the bearing disc 9, impact force of downward movement of the valve core 4 acts on the upper end of the bearing disc 9, when the impact force is larger than the elastic force of the wave spring 7, the wave spring 7 generates compression deformation, the valve core 4 and the bearing disc 9 move downwards together, and as the elastic force of the wave spring 7 is additionally acted on the valve core 4 and is increased along with the increase of the downward movement distance D (figure 4 b) between the valve core 4 and the bearing disc 9, the kinetic energy of the valve core 4 is converted into elastic potential energy through the elastic deformation of the wave spring 7, so that the downward movement speed of the valve core 4 is greatly reduced; when the valve core 4 continues to descend until the conical surface of the rubber ring 5 contacts with the conical hole surface of the valve seat 6, the valve core 4 also has inertia of downward movement, and the valve core 4 has an impact effect on the rubber ring 5 so that the rubber ring 5 generates compression deformation to absorb part of kinetic energy of the valve core 4 again; when the conical surface of the rubber ring 5 is contacted with the conical hole surface of the valve seat 6, the upper part of the conical disc of the valve core 4 is high pressure, the lower part is low pressure, the pressure difference between the upper part and the lower part of the valve core 4 enables the rubber ring 5 to continuously generate compression deformation, the valve core 4 continuously moves downwards until the conical surface of the valve core 4 is contacted with the conical hole surface of the valve seat 6, and an impact load is also acted on the contact part of the conical surface of the valve core 4 and the conical hole surface of the valve seat 6 at a moment of contact; because the wave spring 7 firstly decelerates the valve core 4 once, the impact load when the rubber ring 5 contacts with the valve seat 6 is reduced, the rubber ring 5 decelerates the valve core 4 again, and the impact load when the conical surface of the valve core 4 contacts with the conical hole surface of the valve seat 6 is small, thereby achieving the purpose of prolonging the service lives of key parts such as the rubber ring 5, the valve core 4, the valve seat 6 and the like.

It is further preferable that the buffer member is a rubber ring 5 based on the foregoing preferred embodiment, and the contact surface between the rubber ring 5 and the valve core 4 protrudes 1-2mm beyond the sealing conical surface of the valve core 4.

Example 2

In fact, the multi-stage buffer structure according to the present embodiment of the invention has an advantage. That is, in the prior art, the single buffer structure is only suitable for the case that the valve core 4 adopts the guide rod, and is not suitable for the claw-shaped guide structure of the valve core 4. The reason is that the claw-shaped guide structure pump valve is large in diameter but small in axial size, and after the large diameter is adopted in the buffer structure of the guide rod pump valve, the rigidity of the buffer piece is large, the buffer effect is poor, and the buffer piece cannot be suitable for the claw-shaped guide structure, so that more complex and flexible buffer measures are required to meet the specific buffer requirement. The multi-stage buffer structure in this embodiment can adapt to the valve core 4 with different guiding structures, including the case of adopting the claw-shaped guiding structure, through the combination of the bottom buffer member 7, the side buffer member 5 and the top buffer member 2, thereby providing wider applicability and application flexibility. This is one of the advantages of the multi-stage buffer structure of the present embodiment.

Therefore, the valve core 4 in the embodiment is a claw valve core 4, one end of the claw valve core 4 is fixedly connected to the bearing disc 9, the inner diameter of the bottom buffer member 7 is 5-6mm larger than the inner diameter of the bearing disc 9, the outer cylinder diameter of the bearing disc 9 is 8-10mm larger than the inner hole diameter of the valve seat 6 and is in clearance fit with the inner cylinder diameter of the bearing disc 9, and the bearing disc 9 moves up and down freely in a clearance space during buffering. The foregoing structure can be understood with reference to fig. 3.

It will be appreciated that due to the large diameter and small axial dimension of the claw spool 4, the claw spool 4 is more complex and requires a higher damping structure than conventional pilot rod structures. The buffering structure in this embodiment uses the wave spring 7 as the bottom buffering member 7 through the larger inner diameter of the bottom buffering member 7, the larger outer cylinder diameter of the bearing disc 9 and the clearance fit between the bearing disc and the inner hole of the valve seat 6, so that the buffering requirement of the claw valve core 4 can be met, the valve core 4 can be effectively buffered and protected in the closing process, and the valve core is suitable for application occasions of the claw valve core 4. This is one of the reasons why the foregoing structure is applied to the claw valve element 4 in the present embodiment.

The inner diameter of the bottom cushion 7 described in the foregoing embodiment is thus 5-6mm larger than the inner diameter of the thrust plate 9, and the outer cylindrical diameter of the thrust plate 9 is 8-10mm larger than the inner diameter of the valve seat 6, with reference to fig. 5 for a specific construction. And adopts clearance fit with the buffer disk, so that the buffer disk can freely move up and down in the clearance space. The design can provide enough buffer space and freedom degree in the movement process of the claw valve core 4, so that the impact force and vibration of the valve core 4 in the closing process can be effectively relieved, and excessive collision and abrasion between the valve core 4 and the valve seat 6 are avoided.

In combination with the description of the preferred embodiment of embodiment 1 and the previous embodiment, the applicant proposes a further preferred embodiment based on this, the structure of which is understood with reference to fig. 1, in this embodiment, when the clearance between the side buffer 5 and the valve core 4 is 1-2mm, the claw-shaped end of the valve core 4 is just contacted by the bearing disc 9, and the bottom buffer 7 (and the wave spring 7) is contacted by the bearing disc 9, so that the bottom buffer 7 starts to bear the impact of the valve core 4.

In this embodiment, the bottom buffer member 7 is a wave spring 7, and the specific structure is shown in fig. 6, and the rubber cover is sleeved in a groove at the upper part of the claw-shaped valve core 4 to form a claw-shaped valve core 4 assembly and can move up and down in the valve seat 6; the rubber tightly holds the contact part of the claw-shaped valve core 4 under the elastic action of the self material, and the lower conical surface of the rubber protrudes 1-2mm more than the sealing conical surface of the claw-shaped valve core 4;

the valve seat 6, the wave spring 7, the fixed screw sleeve 8 and the bearing disc 9 form a valve seat 6 assembly, and are fixed on the pump head by the conical surface outside the valve seat 6; the conical surface at the upper part of the valve seat 6 is a sealing surface contacted with the conical surface of the claw-shaped valve core 4 and the conical surface of the rubber sheet, the smallest inner hole is a guide hole for the claw-shaped valve core 4 to move up and down, the lower part is provided with a unthreaded hole and a threaded hole, and the small diameter of the threaded hole is 4-6mm larger than the diameter of the unthreaded hole so as to ensure that the bearing disc 9 can be installed in the unthreaded hole from the lower part; during assembly, the bearing disc 9 is firstly arranged in a smooth hole at the lower part of the valve seat 6, then the wave spring 7 is arranged, the fixing screw sleeve 8 is screwed tightly, and then the fixing screw sleeve 8 is prevented from loosening by spot welding or punching riveting.

When the distance from the stepped annular surface of the unthreaded hole formed in the lower part of the valve seat 6 to the upper end surface of the valve seat 6 is required to ensure that the lower end surface of the guide part of the claw-shaped valve core 4 is contacted with the bearing disc 9, the rubber and the sealing conical surface piece of the valve seat 6 have a gap of 1-2mm, and the downward impact of the claw-shaped valve core 4 is ensured to act on the bearing disc 9 at first.

The outer diameter of the wave spring 7 is in clearance fit with an unthreaded hole on the valve seat 6 matched with the bearing disc 9, so that the wave spring 7 can deform freely when compressed; the inner diameter of the wave spring 7 is 5-6mm larger than the inner hole diameter of the bearing disc 9;

the diameter of the outer cylinder of the bearing disc 9 is 8-10mm larger than that of the guide hole of the valve seat 6, and the bearing disc 9 and the assembly cylindrical unthreaded hole of the valve seat 6 are in clearance fit, so that the bearing disc 9 can move up and down freely when being impacted by the claw-shaped valve core 4; the diameter of the inner hole of the bearing disc 9 is 5-6mm larger than the inner diameter of the end face of the guide part of the claw-shaped valve core 4; the upper surface of the bearing plate 9 is made of impact-resistant materials.

The diameter of the inner hole of the fixed screw sleeve 8 is the same as that of the inner hole of the bearing disc 9, a plurality of round holes are uniformly distributed on the circular ring of the fixed screw sleeve 8, and a tool is inserted into the round holes to screw the fixed screw sleeve 8 during assembly.

The pressure cap 1, the spring seat 2, the conical compression spring 3, the claw-shaped valve core 4 and the rubber adopt the existing reciprocating pump valve structure.

The outer cone, the positioning step and other outer structures of the valve seat 6 adopt the same structure as the existing pump valve, and the pump valve can be used by directly replacing the existing pump valve assembly or only replacing the valve seat 6 of the existing pump valve under the condition that the installation structure and the size of the existing pump valve of the pump head of the reciprocating pump are not required to be changed.

In fact, in the foregoing embodiment, the stiffness of the wave spring 7 is selected to be appropriate according to the mass of the claw valve core 4 and the working pressure of the reciprocating pump, the wave spring 7 comprises different models, and the more the wave number is, the more the stiffness of the wave spring 7 is under the condition of adopting the same inner diameter, outer diameter and plate thickness. The larger the pump valve diameter, the larger the impact load, and the larger the stiffness of the damper wave spring 7 should be selected. Such as: when the diameter of the pump valve is 4', a wave spring 7 with the wave number of 4 can be selected; when the diameter of the pump valve is 5', a wave spring 7 with the wave number of 6 can be selected; when the diameter of the pump valve is 6', a wave spring 7 with the wave number of 8 can be selected.

It will be appreciated that the height of the wave spring 7 is selected so that a certain pre-compression is created after it has been fitted into the valve seat 6, ensuring that the wave spring 7 does not rotate under the action of the high-velocity fluid. After the wave spring 7 is adopted, the height of the spring is far smaller than that of other compression springs such as a coil spring and the like, and the rigidity of the spring is also far smaller than that of a belleville spring, so that the impact energy of the claw-shaped valve core 4 can be effectively absorbed, and the height of the valve seat 6 can be effectively controlled.

The above is only an example portion of the application and is not intended to limit the application in any way. Any simple modification, equivalent variation and modification of the above embodiments still fall within the scope of the protection of the technical solution of this application.

Claims (8)

1. The utility model provides a jumbo size reciprocating pump valve with multistage buffering function, includes pressure cap, spring holder, toper compression spring, the disk seat that connects gradually, open at the disk seat center has the disk seat hole, but the case of axial displacement is put to disk seat hole cover, the case with be equipped with multistage bolster between the disk seat, its characterized in that, multistage bolster includes: the bottom buffer piece, the side buffer piece and the top buffer piece are coaxially and sequentially arranged with the movement of the valve core, the bottom buffer piece is arranged on at least one side buffer piece of a plane where the valve seat reaches corresponding to the limit of the falling-back progress of the valve core, the side buffer piece extends out of a non-axial extension part, the extension part is embedded with the inner hole of the valve seat, and two ends of the top buffer piece are fixedly connected with the spring seat and the valve core.

2. The large-sized reciprocating pump valve with multi-stage buffering function according to claim 1, wherein: gaps are reserved at the connection or embedding positions of the bottom buffer piece and the side buffer piece and the valve seat, the gaps gradually decrease from one end close to the spring seat to a far away section, and the buffer pieces of all stages are buffered in sequence due to different contact sequences in the buffering process.

3. The large-sized reciprocating pump valve with multi-stage buffering function according to claim 2, wherein: the gap reduction between each adjacent bumper is 1-2mm.

4. A large-sized reciprocating pump valve with multi-stage buffering function according to claim 3, characterized in that: the valve seat is characterized in that the side buffer piece is one, one side of the side buffer piece is attached to the tail end of the valve seat near the spring seat section, the other side of the side buffer piece is an extending part integrally connected to the valve core, the extending part and the tail end of the valve seat form an embedded structure, and the inclination angle of an attaching surface between the side buffer piece and the tail end of the valve seat relative to a horizontal plane is 30-45 degrees.

5. The large-sized reciprocating pump valve with multi-stage buffering function according to claim 4, wherein: the buffer piece is a rubber ring, and the contact surface of the rubber ring and the valve core protrudes 1-2mm more than the sealing conical surface of the valve core.

6. The large-sized reciprocating pump valve with multi-stage buffering function according to claim 2, wherein: the valve core is a claw-shaped valve core, the claw-shaped end of the claw-shaped valve core gradually approaches the bearing disc in the falling process of the valve core, the claw-shaped end of the valve core contacts with the bearing disc when the pump valve is completely closed, the inner diameter of the bottom buffer piece is 5-6mm larger than that of the bearing disc, the outer cylinder diameter of the bearing disc is 8-10mm larger than that of the inner hole of the valve seat and is in clearance fit with the inner hole of the valve seat, and the bearing disc moves freely up and down in a clearance space during buffering.

7. The large-sized reciprocating pump valve with multi-stage buffering function according to claim 6, wherein: the bottom buffer piece is a wave spring, the wave spring comprises different types, the wave spring stiffness of the different types is matched with the diameter of a different pump valve, and the stiffness and the diameter of the pump valve are synchronously increased.

8. The large-sized reciprocating pump valve with multi-stage buffering function according to claim 7, wherein: and when the valve is static, the gap between the side buffer piece and the valve seat is 1mm, and the bottom buffer piece is in direct contact with the valve core, namely the bearing disc is in direct contact with the wave spring.