CN220185480U

CN220185480U - High-pressure supercharger with floating supercharging part

Info

Publication number: CN220185480U
Application number: CN202321965306.1U
Authority: CN
Inventors: 胡方
Original assignee: Individual
Current assignee: Individual
Priority date: 2023-07-25
Filing date: 2023-07-25
Publication date: 2023-12-15
Anticipated expiration: 2033-07-25

Abstract

The utility model provides a floating type high-pressure booster of a booster part, which comprises a booster cylinder and a hydraulic cylinder, wherein the booster cylinder comprises a high-pressure cylinder body and a piston assembly, and the piston assembly is provided with a liquid channel for liquid to enter and exit the high-pressure cylinder body; the piston assembly is connected with the cylinder body of the hydraulic cylinder, the piston assembly is sleeved on one side of the high-pressure cylinder body, and the high-pressure cylinder body can axially move relative to the piston assembly along the high-pressure cylinder body; the other side of the high-pressure cylinder body is connected with a piston rod of the hydraulic cylinder, and the high-pressure cylinder body and the piston rod are connected in a non-rigid mode; according to the design, the high-pressure cylinder body is used as a movable piece to perform axial reciprocating motion, the high-pressure cylinder body and a piston rod of the hydraulic cylinder do the same-direction motion, and the high-pressure cylinder body does not have axial circulating stress, so that the service life of the high-pressure cylinder body is prolonged; according to the hydraulic cylinder, the high-pressure cylinder body is not rigidly connected with the piston rod of the hydraulic cylinder, force transmission can be achieved through the piston rod and the high-pressure cylinder body without concentricity, eccentric force is not applied to the sealing piece of the pressurizing cylinder, and the processing and assembling requirements are greatly reduced.

Description

High-pressure supercharger with floating supercharging part

Technical Field

The utility model relates to the technical field of supercharging equipment, in particular to a floating type high-pressure supercharger with a supercharging part.

Background

The booster is a key device commonly used in applications such as water jet cutting, high-pressure homogenization, high-pressure hydraulic pumps and the like, is used as an effective energy conversion device, and can convert low-pressure hydraulic oil input by a hydraulic end into an ultrahigh-pressure material flow of an output end.

The booster comprises a booster cylinder and a hydraulic cylinder, wherein a piston rod of the hydraulic cylinder is directly connected with a booster rod of the booster cylinder, the piston rod and the booster rod are coaxially designed, and the booster rod is driven by the hydraulic cylinder to reciprocate along the axial direction of the booster cylinder. However, due to the limitation of part design errors and assembly errors, the piston rod and the pressurizing rod cannot be 100% concentric, so that when the pressurizing rod reciprocates, the sealing is quickly failed due to eccentric force on a sealing element of the pressurizing cylinder. When the supercharger works, the compression rod reciprocates along the axial direction, and the cylinder body of the supercharging cylinder can continuously receive axial cyclic stress, so that the cylinder body of the supercharging cylinder is easy to fatigue and damage.

Disclosure of Invention

In order to overcome the problems in the related art, the utility model provides the floating type high-pressure booster with the booster part, which is characterized in that the high-pressure cylinder body is used as a movable part to axially reciprocate, the high-pressure cylinder body does not have axial circulating stress, the high-pressure cylinder body is not rigidly connected with a piston rod of a hydraulic cylinder, the piston rod and the high-pressure cylinder body can realize force transmission without concentricity, the sealing part of the booster cylinder is not subjected to eccentric force, and the processing and assembly requirements are greatly reduced.

The utility model aims to provide a floating type high-pressure booster with a booster part, which comprises a booster cylinder and a hydraulic cylinder, wherein the booster cylinder comprises a high-pressure cylinder body and a piston assembly, and the piston assembly is provided with a liquid channel for liquid to enter and exit the high-pressure cylinder body;

the piston assembly is connected with the cylinder body of the hydraulic cylinder, the piston assembly is sleeved on one side of the high-pressure cylinder body, and the high-pressure cylinder body can axially move relative to the piston assembly along the high-pressure cylinder body;

the other side of the high-pressure cylinder body is connected with a piston rod of the hydraulic cylinder, and the high-pressure cylinder body and the piston rod are connected in a non-rigid connection mode.

In the preferred technical scheme of the utility model, a through type pressurizing inner cavity is formed in the middle part in the high-pressure cylinder body along the axial direction, the piston assembly comprises a sealing column, the high-pressure cylinder body is sleeved on the sealing column, the high-pressure cylinder body is connected with the piston rod through a force transmission block, the force transmission block and the sealing column are in sealing fit with the pressurizing inner cavity, the force transmission block is abutted with the high-pressure cylinder body, and the connecting and fit mode of the force transmission block and the piston rod is non-rigid connection.

In the preferred technical scheme of the utility model, an inner sleeve body is coaxially nested in the high-pressure cylinder body, the inner sleeve body is in interference fit with the high-pressure cylinder body, and a pressurizing inner cavity is formed in the inner wall of the inner sleeve body.

In the preferred technical scheme of the utility model, the sleeve is sleeved outside the high-pressure cylinder body, the sealing column is fixedly connected with the sleeve, and the sleeve is arranged on the cylinder body of the hydraulic cylinder.

In the preferred technical scheme of the utility model, a rod body coaxially penetrates through the sealing column, a piston part is arranged at the inner end of the rod body, the outer end of the sealing column is in threaded connection with the sleeve, an external thread is arranged at the outer end of the rod body, a nut is in threaded connection with the outer end of the rod body, and the nut abuts against the outer end of the sealing column.

In the preferred technical scheme of the utility model, a sealing ring A is sleeved at the inner end of the rod body, and the sealing ring A is positioned between the sealing column and the piston part.

In the preferred technical scheme of the utility model, a plug part capable of being inserted into the pressurizing inner cavity is arranged at the inner end of the force transmission block, and a sealing ring B is arranged at the periphery of the plug part.

In the preferred technical scheme of the utility model, the outer end of the force transmission block is abutted with the piston rod.

In the preferred technical scheme of the utility model, the tail end of the piston rod is provided with a central notch, the outer end of the force transmission block is provided with a convex column, the convex column is sleeved in the central notch, the outer diameter of the convex column is smaller than the inner diameter of the central notch, and the piston rod is hinged with the convex column through a radial pin shaft.

In the preferred technical scheme of the utility model, the force transmission block is embedded with a magnet, and the magnet is magnetically attracted with the end face of the high-pressure cylinder body.

The beneficial effects of the utility model are as follows:

the high-pressure cylinder body is used as a movable piece to perform axial reciprocating motion, the high-pressure cylinder body and a piston rod of the hydraulic cylinder do the same-direction motion, and the high-pressure cylinder body does not have axial circulating stress, so that the service life of the high-pressure cylinder body is prolonged;

the high-pressure cylinder body is not rigidly connected with the piston rod of the hydraulic cylinder, the piston rod and the high-pressure cylinder body can realize force transmission without concentricity, and the sealing element of the pressurizing cylinder is not subjected to eccentric force, so that the processing and assembling requirements are greatly reduced;

the quick conversion of the supercharging ratio can be realized by replacing high-pressure cylinders with different inner diameters and correspondingly adapted piston assemblies;

by adopting a floating dynamic sealing structure, the sealing element can be quickly replaced.

Drawings

Fig. 1 is a schematic view of a structure of a high-pressure supercharger in which a supercharging portion floats.

Fig. 2 is a structural cross-sectional view of a high-pressure supercharger with a floating supercharger.

Fig. 3 is a schematic diagram of the mating structure of the piston assembly and the high pressure cylinder.

Fig. 4 is a schematic diagram of the mating structure of the force transfer block and the high pressure cylinder.

Fig. 5 is an exploded view of a partial structure.

Reference numerals:

100. a hydraulic cylinder; 110. a cylinder; 120. a piston rod; 121. a central slot; 200. a pressurizing cylinder; 210. a high pressure cylinder; 220. an inner sleeve body; 230. a pressurized inner cavity; 240. a piston assembly; 241. a liquid channel; 242. a sealing column; 243. a rod body; 244. a nut; 245. a piston section; 246. a sealing ring A; 250. a force transmission block; 251. a sealing ring B; 252. a convex column; 253. briquetting; 300. a connecting piece; 310. a sleeve.

Detailed Description

Preferred embodiments of the present utility model will be described in more detail below with reference to the accompanying drawings. While the preferred embodiments of the present utility model are shown in the drawings, it should be understood that the present utility model may be embodied in various forms and should not be limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the scope of the utility model to those skilled in the art.

In the prior art, the supercharger comprises a supercharging cylinder and a hydraulic cylinder, wherein a piston rod of the hydraulic cylinder is directly connected with a supercharging rod of the supercharging cylinder, the piston rod and the supercharging rod are coaxially designed, and the supercharging rod is driven by the hydraulic cylinder to reciprocate along the axial direction of the supercharging cylinder. However, due to the limitation of part design errors and assembly errors, the piston rod and the pressurizing rod cannot be 100% concentric, so that when the pressurizing rod reciprocates, the sealing is quickly failed due to eccentric force on a sealing element of the pressurizing cylinder. When the supercharger works, the compression rod reciprocates along the axial direction, and the cylinder body of the supercharging cylinder can continuously receive axial cyclic stress, so that the cylinder body of the supercharging cylinder is easy to fatigue and damage.

Example 1

In view of the above, embodiment 1 provides a high-pressure supercharger with a floating supercharging portion.

As shown in fig. 1-5, a floating high pressure booster of a booster part comprises a booster cylinder 200 and a hydraulic cylinder 100, wherein the booster cylinder 200 comprises a high pressure cylinder body 210 and a piston assembly 240, and the piston assembly 240 is provided with a liquid channel 241 for liquid to enter and exit the high pressure cylinder body 210;

the piston assembly 240 is connected with the cylinder body 110 of the hydraulic cylinder 100, the piston assembly 240 is sleeved on one side of the high-pressure cylinder body 210, and the high-pressure cylinder body 210 can axially move along the high-pressure cylinder body 210 relative to the piston assembly 240; specifically, the booster cylinder 200 and the hydraulic cylinder 100 are sequentially arranged, the front end of the piston assembly 240 is positioned at the front side of the high-pressure cylinder body 210 and is fixedly connected with the cylinder body 110 of the hydraulic cylinder 100 positioned at the rear side of the high-pressure cylinder body 210 through the connecting piece 300, the rear end of the piston assembly 240 is sleeved in the high-pressure cylinder body 210, and the structural design enables the high-pressure cylinder body 210 to axially reciprocate as a movable piece, so that no axial circulating stress exists on the high-pressure cylinder body 210, and the service life of the high-pressure cylinder body 210 is prolonged;

the piston rod 120 of the hydraulic cylinder 100 is connected to the opposite side of the high-pressure cylinder body 210, the connection and matching mode of the high-pressure cylinder body 210 and the piston rod 120 is non-rigid connection, the structural design enables the piston rod 120 and the high-pressure cylinder body 210 to realize force transmission without concentricity, eccentric force is not applied to sealing elements of the booster cylinder 200, and machining and assembling requirements are greatly reduced.

In practical application, the rear end of the liquid channel 241 is located in the high-pressure cylinder 210, the front end is located outside the high-pressure cylinder 210, and the end outside the cylinder is communicated with a feeding pipe with a one-way valve and a discharge port with a one-way valve, wherein the one-way valve of the feeding pipe can only allow materials to enter the liquid channel 241, and the one-way valve of the discharge port can only allow materials to be output from the discharge port.

In practical application, the quick conversion of the supercharging ratio can be realized by replacing the high-pressure cylinders with different inner diameters and the correspondingly adapted piston assemblies 240.

When in use, the piston assemblies 240 of the hydraulic cylinder 100 and the booster cylinder 200 are used as fixed parts, the high-pressure cylinder body 210 is used as movable parts to axially move, and the high-pressure cylinder body 210 and the piston rod 120 of the hydraulic cylinder 100 move in the same direction, so that in the use process, no axial circulating stress exists on the high-pressure cylinder body 210, and the service life of the high-pressure cylinder body 210 is prolonged. The connection and matching mode of the high-pressure cylinder body 210 and the piston rod 120 is non-rigid connection, and when the hydraulic cylinder is used, the piston rod 120 and the high-pressure cylinder body 210 can realize force transmission without concentricity, so that the sealing element of the booster cylinder 200 is not subjected to eccentric force during working, and the processing and assembling requirements are greatly reduced.

Example 2

Further, embodiment 2 provides a concrete mating structure example of the high-pressure cylinder and the remaining components on the basis of embodiment 1.

As shown in fig. 2-5, a through-type pressurizing inner cavity 230 is formed in the middle part in the high-pressure cylinder 210 along the axial direction, the piston assembly 240 includes a sealing post 242, the high-pressure cylinder 210 is sleeved on the sealing post 242, the high-pressure cylinder 210 is connected with the piston rod 120 through a force transmission block 250, the force transmission block 250 and the sealing post 242 are in sealing fit with the pressurizing inner cavity 230, the force transmission block 250 is abutted to the high-pressure cylinder 210, and the force transmission block 250 is connected with the piston rod 120 in a non-rigid connection manner.

In this embodiment, an inner sleeve 220 is coaxially nested in the high-pressure cylinder 210, the inner sleeve 220 is in interference fit with the high-pressure cylinder 210, and a pressurizing inner cavity 230 is formed on the inner wall of the inner sleeve 220. The inner sleeve 220 is made of different materials from the high-pressure cylinder 210, and various ceramics or other hard alloys can be selected to manufacture the inner sleeve 220 according to the requirements of actual working application scenes.

In this embodiment, the connecting member 300 is a sleeve 310, the high-pressure cylinder 210 is sleeved with the sleeve 310, the front end of the sealing post 242 is fixedly connected with the front end of the sleeve 310, the rear end of the sleeve 310 is provided with a flange portion, and the flange portion is connected with the front end of the cylinder body 110 of the hydraulic cylinder 100 through bolts. In practical applications, the high-pressure cylinder 210 may be directly slidably engaged with the sleeve 310, or a guide rail axially disposed along the sleeve 310 may be disposed on the inner wall of the sleeve 310, and a connection structure slidably engaged with the guide rail may be disposed on the outer wall of the high-pressure cylinder 210, so as to improve the stability of axial movement of the high-pressure cylinder 210. The connection structure may be a slider or a chute, for example.

In this embodiment, a rod body 243 coaxially penetrates through the sealing post 242, a piston portion 245 is disposed at the inner end of the rod body 243, a sealing ring a246 is sleeved at the inner end of the rod body 243, the sealing ring a246 is located between the sealing post 242 and the piston portion 245, the outer end of the sealing post 242 is screwed with the sleeve 310, an external thread is disposed at the outer end of the rod body 243, a nut 244 is screwed at the outer end of the rod body 243, and the nut 244 abuts against the outer end of the sealing post 242. This design has formed a floating dynamic seal structure, during the use, can make piston portion 245 axial displacement through rotatory nut 244 to carry out the wear compensation to sealing washer A246, simultaneously, piston portion 245 atress back, can compress tightly sealing washer A246 all the time, thereby guarantee sealed reliability. Meanwhile, due to the design that the outer end of the sealing post 242 is in threaded connection with the sleeve 310, the quick maintenance and replacement of the sealing ring A246 can be realized only by unscrewing and withdrawing the rod 243.

In this embodiment, the inner end of the force-transmitting block 250 is provided with a plug portion capable of being inserted into the pressurizing cavity 230, the periphery of the plug portion is provided with a sealing ring B251, the sealing ring B251 is arranged on the periphery of the end face of the plug portion, or, as shown in fig. 4, the sealing ring B251 is arranged between the plug portion and the pressing block 253, the middle part of the pressing block 253 is sleeved on the plug portion through a central rod, the sealing ring B251 is sleeved on the central rod, and the tail end of the central rod is locked with the force-transmitting block 250 through a screw. When the sealing device is used, the pressing block 253 can be axially moved through rotation, so that the sealing ring B251 is pressed for wear compensation, and meanwhile, after the pressing block 253 is stressed, the sealing ring B251 is always pressed, so that the sealing reliability is ensured. The design forms a floating static sealing structure, and when in use, the sealing ring B251 can always keep sealing with the pressurizing inner cavity 230 under the stress deformation. Meanwhile, the plug part is only required to be pulled out, so that the quick maintenance and replacement of the sealing ring B251 can be realized.

In this embodiment, a magnet may be embedded on the force transfer block 250, and the magnet magnetically attracts the end surface of the high pressure cylinder 210, so as to realize the installation and fixation of the force transfer block 250 and the high pressure cylinder 210.

Example 3

Further, embodiment 3 gives a specific structural example of a non-rigid connection on the basis of embodiment 2.

In this embodiment, the outer end of the force transfer block 250 abuts against the piston rod 120, and in this structural design, force is transferred between the force transfer block 250 and the piston rod 120 only through abutting, the force transfer block 250 is in plane contact with the high-pressure cylinder 210, and whether the force transfer block 250 is coaxial with the piston rod 120 or not does not affect force transfer, so that force transfer can be achieved without concentricity between the piston rod 120 and the high-pressure cylinder 210, and the sealing element of the booster cylinder 200 is not subjected to eccentric force during operation, thereby greatly reducing processing and assembly requirements.

When in use, when the piston rod 120 extends out, the high-pressure cylinder body can be pushed to move through the force transmission block 250 so as to compress materials in the high-pressure cylinder body and realize supercharging output; after the pressurization output, new materials enter the high-pressure cylinder body, the high-pressure cylinder body is pushed to move reversely, and the piston rod 120 is pushed to retract through the force transmission block 250 while the high-pressure cylinder body moves reversely.

Example 4

Further, embodiment 4 gives a specific structural example of another non-rigid connection on the basis of embodiment 2.

In this embodiment, as shown in fig. 4-5, a central notch 121 is provided at the end of the piston rod 120, a boss 252 is provided at the outer end of the force transmission block 250, the boss 252 is sleeved in the central notch 121, the outer diameter of the boss 252 is smaller than the inner diameter of the central notch 121, and the piston rod 120 is hinged with the boss 252 via a radial pin. Because the outer diameter of the convex column 252 is smaller than the inner diameter of the central notch 121, in the use process, the force transfer block 250 is in plane contact with the high-pressure cylinder body 210, and whether the force transfer block 250 is coaxial with the piston rod 120 or not can not affect the force transfer, so that the piston rod 120 and the high-pressure cylinder body 210 can realize the force transfer without concentricity, the sealing element of the booster cylinder 200 is not subjected to eccentric force in the working process, and the processing and assembly requirements are greatly reduced.

When in use, when the piston rod 120 extends out, the high-pressure cylinder body can be pushed to move through the force transmission block 250 so as to compress materials in the high-pressure cylinder body and realize supercharging output; when the piston rod 120 is retracted, the high pressure cylinder can be pulled to move by the force transfer block 250 so that new material is drawn into the high pressure cylinder.

The relative arrangement of the components and steps, numerical expressions and numerical values set forth in these embodiments do not limit the scope of the present utility model unless it is specifically stated otherwise. Meanwhile, it should be understood that the sizes of the respective parts shown in the drawings are not drawn in actual scale for convenience of description. Techniques, methods, and apparatus known to one of ordinary skill in the relevant art may not be discussed in detail, but should be considered part of the specification where appropriate. In all examples shown and discussed herein, any specific values should be construed as merely illustrative, and not a limitation. Thus, other examples of the exemplary embodiments may have different values. It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further discussion thereof is necessary in subsequent figures.

In the description of the present utility model, it should be understood that the azimuth or positional relationships indicated by the azimuth terms such as "front, rear, upper, lower, left, right", "horizontal direction, vertical, horizontal", and "top, bottom", etc., are generally based on the azimuth or positional relationships shown in the drawings, merely to facilitate description of the present utility model and simplify the description, and these azimuth terms do not indicate and imply that the apparatus or elements referred to must have a specific azimuth or be constructed and operated in a specific azimuth, and thus should not be construed as limiting the scope of protection of the present utility model; the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.

The above description is only of the preferred embodiments of the present utility model and is not intended to limit the present utility model, but various modifications and variations can be made to the present utility model by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model should be included in the protection scope of the present utility model.

Claims

1. The utility model provides a floating high pressure booster of booster part, includes booster cylinder and pneumatic cylinder, its characterized in that:

the pressurizing cylinder comprises a high-pressure cylinder body and a piston assembly, wherein the piston assembly is provided with a liquid channel for liquid to enter and exit the high-pressure cylinder body;

2. The booster-floating high-pressure booster according to claim 1, wherein:

the middle part has offered the pressure boost inner chamber of through-type along the axial in the high pressure cylinder body, the piston subassembly includes the seal post, and high pressure cylinder body cover is established on the seal post, is connected through the biography power piece between high pressure cylinder body and the piston rod, biography power piece, seal post all with pressure boost inner chamber sealing fit, biography power piece and high pressure cylinder body butt, the connection fit mode of biography power piece and piston rod is non-rigid connection.

3. The booster-floating high-pressure booster according to claim 2, wherein:

an inner sleeve body is coaxially nested in the high-pressure cylinder body, the inner sleeve body is in interference fit with the high-pressure cylinder body, and a pressurizing inner cavity is formed in the inner wall of the inner sleeve body.

4. The booster-floating high-pressure booster according to claim 2, wherein:

the high-pressure cylinder body is sleeved with a sleeve, the sealing column is fixedly connected with the sleeve, and the sleeve is arranged on the cylinder body of the hydraulic cylinder.

5. The booster-floating high-pressure booster according to claim 4, wherein:

the sealing post is characterized in that a rod body coaxially penetrates through the sealing post, a piston part is arranged at the inner end of the rod body, the outer end of the sealing post is in threaded connection with the sleeve, an external thread is arranged at the outer end of the rod body, a nut is in threaded connection with the outer end of the rod body, and the nut abuts against the outer end of the sealing post.

6. The booster-floating high-pressure booster according to claim 5, wherein:

and a sealing ring A is sleeved at the inner end of the rod body and is positioned between the sealing column and the piston part.

7. The booster-floating high-pressure booster according to claim 2, wherein:

the inner end of the force transmission block is provided with a plug part which can be inserted into the pressurizing inner cavity, and the periphery of the plug part is provided with a sealing ring B.

8. The booster-floating high-pressure booster according to claim 7, wherein:

the outer end of the force transmission block is abutted with the piston rod.

9. The booster-floating high-pressure booster according to claim 7, wherein:

the end of the piston rod is provided with a central notch, the outer end of the force transmission block is provided with a convex column, the convex column is sleeved in the central notch, the outer diameter of the convex column is smaller than the inner diameter of the central notch, and the piston rod is hinged with the convex column through a radial pin shaft.

10. The booster-floating high-pressure booster according to claim 2, wherein:

and the force transmission block is embedded with a magnet, and the magnet is magnetically attracted with the end face of the high-pressure cylinder body.