Container type semi-solid muddy filler sealing device for fluid equipment

Abstract

The utility model relates to an integrated packing sealing device for fluid equipment. The integrated packing sealing device comprises a shaft sleeve, a locking ring, a formed sealing ring assembly, semi-solid muddy packing, a cylindrical main gland and an annular auxiliary gland which are installed around a rotating shaft. A main gland cylinder is formed at the front end of the main gland, and a main gland step extending outwards relative to the main gland cylinder is formed at the rear end of the main gland. A main gland step configured to be fastened to a rear wall surface of the device housing around the orifice, the main gland cylinder passing through the orifice, a gap being formed between an outer peripheral surface of the main gland cylinder and an inner wall surface of the device housing forming the orifice, in which a fluid is allowed to flow; the inner circumferential surface of the main gland cylinder forms a cylindrical space around the outer circumferential surface of the shaft sleeve, the molded sealing ring assembly and the filler are filled in the cylindrical space, and the filler can flow in the cylindrical space; the shaped seal ring assembly includes a first shaped seal ring and a second shaped seal ring with a filler therebetween. According to the sealing device, the reliability and safety of the sealing device can be improved.

Description

Technical Field

[0001] The present application relates to fluid sealing technology, and in particular to a containerized semi-solid mud-like filler sealing device for fluid equipment. Background Art

[0002] In industrial continuous production, a large amount of fluid (including gas, a mixture of gas and liquid, and especially liquid) needs to be transported through a pump or other fluid equipment. The pump generally includes a pump casing and a rotating shaft. The rotating shaft passes through the orifice of the pump casing and rotates at high speed during operation to transport the fluid in the pump casing or pressurize the fluid. Therefore, an effective sealing device is provided between the orifice and the rotating shaft to prevent the fluid from leaking from the orifice, which contributes to the safe operation of the pump. Most of the shutdown maintenance of the pump is to replace the failed sealing device. In the prior art, the sealing forms of the sealing device include mechanical seals, packing seals, and layered shear packing seals. Mechanical seals are defined in relevant national standards as: a device for preventing fluid leakage composed of at least one pair of end faces perpendicular to the axis of rotation, which are kept in contact and slide relative to each other under the action of fluid pressure and the elastic force or magnetic force of the compensation mechanism and the cooperation of auxiliary seals.

[0003] Mechanical seals are made of rigid materials, offering excellent sealing performance and long life. They require high precision in use and machining, but are expensive and difficult to repair and replace. Packing seals utilize pressure from fixed components to plastically deform the packing, generating radial force that creates a tight seal with the shaft. Early packing seals wore the shaft, required flushing, and exhibited minor leaks. However, these seals were inexpensive and simple to repair and replace. Later, sleeves were added to address shaft wear, and sleeves, packing, and glands were assembled into a single unit through radial connections for easy replacement, such as the cartridge packing seal structure disclosed in patent publication CN114688073A. However, these improvements did not address the high wear and tear of packing seals, resulting in the frequent downtime required for seal replacement.

[0004] Layered shear packing seal is a new sealing method. Chinese patent CN215672853U discloses a layered shear packing seal for pumps. It uses isolation of bottom rings at both ends and fills the middle with semi-solid packing to achieve sealing through internal layering of the sealing packing. However, since the sealing object is a semi-solid packing, the sealing packing is prone to shape changes when subjected to external forces, and its pressure resistance is not high. Therefore, when the fluid equipment has pressure fluctuations and vibration conditions, there is a risk of sealing packing running, leaking, or the sealing layer being damaged and missing, which will lead to sealing failure.

[0005] Subsequent improvements include a container-type composite dynamic seal structure disclosed in Chinese patent CN201875137U and a skeleton-type pump layered shear seal disclosed in Chinese patent CN215672853U. The equipment housing is connected to an external sealing box or sealing cavity, and a muddy or layered shear sealing packing is arranged in the cavity. The compressive performance of the sealing packing is improved by adding a skeleton in or outside the packing. Compared with the packing sealing technology, the layered shear packing sealing technology has the advantages of no shaft wear, no need for flushing water, no specification restrictions, online maintenance, and easy installation. However, the existing technology still has technical deficiencies and technical defects. Since the sealing mechanism of the layered shear packing or muddy packing is to achieve sealing through internal layering of the sealing packing, part of the packing needs to tightly wrap the rotating shaft and rotate with the shaft. During equipment maintenance, this part of the packing cannot be removed or reused from the shaft as a whole, and often requires destructive disassembly. After maintenance and replacement of other mechanical parts of the equipment, the packing is replaced to restore the seal, which increases the cost of equipment operation, as well as the efficiency and labor cost of equipment maintenance. In addition, the existing skeleton technology can only solve the problem of resisting shrinkage under external pressure, but cannot solve the problem of overheating and expansion of the filler, or even seal burning, which is easily caused by the accumulation of internal pressure when the filler is pressurized and replenished during online maintenance.

[0006] With the development of modern industrial technology, mechanical seals have been gradually adopted for fluid conveying equipment facing better working conditions, while packing seals or layered shear packing seals are still required for fluid conveying equipment facing worse working conditions. The fluids under worse working conditions mostly contain mud or foreign particles. When these mud or foreign particles penetrate into the sealing surface, the wear of the rotating shaft and the packing or packing is aggravated, and the sealing effect is damaged, which greatly reduces the service life of the seal and increases the frequency of seal maintenance, seriously affecting the use occasions, service life and sealing effect of the packing seal. These problems cannot be solved by existing technical forms, which hinders the widespread application and economic effect of this sealing technology. Utility Model Content

[0007] One object of the present application is to provide an improved container-type semi-solid mud-like packing sealing device for fluid equipment.

[0008] According to one aspect of the present application, a container-type semi-solid mud packing sealing device for fluid equipment is provided, which is used to seal a rotating shaft passing through an orifice of an equipment casing to prevent the fluid in the equipment casing from leaking from the orifice. The sealing device includes a sleeve installed around the rotating shaft, a locking ring, a molded sealing ring assembly, a semi-solid mud packing, a cylindrical main pressure cover, and an annular secondary pressure cover, wherein: the front end of the main pressure cover forms a main pressure cover cylinder, and the rear end of the main pressure cover forms a main pressure cover step extending outward relative to the main pressure cover cylinder; the main pressure cover step is configured to be fastened to the rear wall surface of the equipment casing around the orifice, and at the same time, the main pressure cover cylinder passes through the orifice, thereby forming a gap between the outer circumferential surface of the main pressure cover cylinder and the inner wall surface of the equipment casing forming the orifice, allowing fluid to flow therein; the inner circumferential surface of the main pressure cover cylinder surrounds the outer circumference of the sleeve The surface forms a cylindrical space, the molded sealing ring assembly and the filler are filled in the cylindrical space, and the filler can flow in the cylindrical space; the main pressure cover step includes a through hole extending from the outer peripheral surface of the main pressure cover step to the inner peripheral surface of the main pressure cover step to communicate with the cylindrical space, and a part of the through hole close to the outer peripheral surface of the main pressure cover step has a threaded joint, which is suitable for connecting to the interface of an external injector or being sealed; the molded sealing ring assembly includes a first molded sealing ring and a second molded sealing ring, and the filler is located between the first molded sealing ring and the second molded sealing ring; the auxiliary pressure cover is fastened to the rear end face of the main pressure cover step by means of a pre-tightening mechanism, so that the front end of the auxiliary pressure cover protrudes axially forward from the rear wall surface of the main pressure cover step into the accommodating space and pushes against the second molded sealing ring; and the locking ring surrounds the rear end of the sleeve and fastens the sleeve to the rotating shaft.

[0009] Optionally, the axial length from the front end face of the first molded sealing ring to the front end face of the main gland step in the cylindrical space is more than twice the axial length from the rear end face of the second molded sealing ring to the front end face of the main gland step.

[0010] Optionally, the sealing device further comprises an additional cylinder integrally formed with the front end of the main gland cylinder, wherein the inner circumference of the additional cylinder forms a spiral groove, or wherein the front end surface of the additional cylinder forms a plurality of grooves extending from the outer circumference of the additional cylinder to the inner circumference of the additional cylinder and arranged at intervals; and / or

[0011] The sealing device also includes an additional sleeve integrally formed with the front end of the sleeve, wherein the outer circumferential surface of the additional sleeve forms a plurality of toothed rings arranged axially at intervals, or wherein the front end surface of the additional sleeve forms a plurality of grooves extending from the outer circumferential surface of the additional sleeve to the inner circumferential surface of the additional cylinder and arranged at intervals.

[0012] Optionally, the starting point of the spiral groove is close to or located at the front end face of the additional cylinder, and the end point of the spiral groove is close to or located at the rear end face of the additional cylinder and is separated from the cylindrical space, and the radial groove depth, axial groove width and / or groove cross-sectional area of ​​the spiral groove remain constant or gradually increase from the starting point to the end point of the spiral groove.

[0013] Optionally, the plurality of tooth rings are separated from the cylindrical space, and each tooth ring has any one of straight tooth shape, oblique tooth shape or spiral tooth shape or a combination thereof.

[0014] Optionally, the sealing device also includes a support skeleton, which includes one or more axial support rods located between the first molded sealing ring and the second molded sealing ring, each axial support rod is suspended in the cylindrical space, and the one or more axial support rods are configured so that the spacing between the first molded sealing ring and the second molded sealing ring can vary between a minimum spacing and a maximum spacing.

[0015] Optionally, the support skeleton also includes a first annular bracket abutting the rear end face of the first molded sealing ring and a second annular bracket abutting the front end face of the second molded sealing ring, and each axial support rod includes a first tip, a first limiting portion protruding relative to the first tip, a second tip and a second limiting portion protruding relative to the second tip, the first tip is slidably inserted into the first annular bracket, and the second tip is slidably inserted into the second annular bracket, so that at the minimum spacing, the first limiting portion abuts against the first annular bracket, and the second limiting portion abuts against the second annular bracket.

[0016] Optionally, the pre-tightening mechanism includes a bolt and a spring sleeved on the bolt, the bolt passes through an axially extending through hole of the secondary pressure cover and is screwed into a threaded hole formed on the rear end face of the main pressure cover step, and the secondary pressure cover is fastened to the main pressure cover with a pre-tightening force provided by the spring compression. At the same time, a certain gap is left between the front end face of the rear end of the secondary pressure cover that does not protrude into the cylindrical space and the rear end face of the main pressure cover step, so that the secondary pressure cover can be axially displaced relative to the main pressure cover, and at the maximum spacing, the spring is fully compressed.

[0017] Optionally, the sealing device further comprises one or more detachable positioning blocks, wherein the one or more positioning blocks are configured to connect the locking ring to the secondary pressure cover to assemble the sealing device together, so that the sealing device can be sleeved on the rotating shaft in one step or the sealing device can be removed from the rotating shaft in one step, and the one or more positioning blocks are configured to be removed from the locking ring and the secondary pressure cover so that the locking ring and the sleeve can rotate with the rotating shaft during operation of the fluid equipment.

[0018] The sealing device provided in the present application can improve the reliability and safety of the device, is easy to install and use, eliminates the sealing failure caused by human installation of the device, facilitates the disassembly and reassembly of the device during maintenance and repair of fluid equipment, and can also solve the problems of short sealing device life and frequent sealing failure in fluids with many impurity particles in poor working conditions, effectively improving the wide application and economic effects of the device. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] The foregoing and other aspects of the present application will be more fully understood from the following detailed description made with reference to the accompanying drawings, in which:

[0020] Figure 1 is a cross-sectional view of a cartridge-type semi-solid mud packing sealing device for fluid equipment according to one embodiment of the present application before being assembled between a rotating shaft and an equipment housing;

[0021] Figure 2 yes Figure 1 a cross-sectional view of the device after being assembled between the rotating shaft and the housing;

[0022] Figure 3 yes Figure 1 An end view of the device;

[0023] Figure 4 yes Figure 1 A partial cross-sectional view of a portion of the device;

[0024] Figure 5 yes Figure 4 A partial cross-sectional view of a portion of the device;

[0025] Figure 6 is a cross-sectional view of a containerized semi-solid mud-like packing sealing device for fluid equipment according to one embodiment of the present application;

[0026] Figure 7 yes Figure 6 A cross-sectional view of a support frame of the device;

[0027] Figure 8 is a cross-sectional view of a containerized semi-solid mud-like packing sealing device for fluid equipment according to one embodiment of the present application;

[0028] Figure 9 is a cross-sectional view of a containerized semi-solid mud-like packing sealing device for fluid equipment according to one embodiment of the present application;

[0029] Figure 10 is a cross-sectional view of a portion of a cartridge-type semi-solid mud-like packing sealing device for fluid equipment according to one embodiment of the present application;

[0030] Figure 11 is a cross-sectional view of a containerized semi-solid mud-like packing sealing device for fluid equipment according to one embodiment of the present application;

[0031] Figure 12 It is a cross-sectional view of a portion of a cartridge-type semi-solid mud packing sealing device for fluid equipment according to one embodiment of the present application. DETAILED DESCRIPTION

[0032] Various exemplary embodiments of the present application will now be described in detail with reference to the accompanying drawings. It should be noted that unless otherwise specifically stated, the relative arrangements of components and steps, numerical expressions and numerical values ​​set forth in these embodiments do not limit the scope of the present application.

[0033] Techniques and equipment known to ordinary technicians in the relevant art may not be discussed in detail, but where appropriate, the techniques and equipment should be considered part of the specification.

[0034] In all examples shown and discussed herein, any specific values ​​should be interpreted as merely exemplary and not limiting. Therefore, other examples of the exemplary embodiments may have different values.

[0035] It should be noted that like reference numerals and letters refer to like items in the following figures, and therefore, once an item is defined in one figure, it need not be further discussed in the following figures.

[0036] like Figure 1 and Figure 2 As shown, the present application generally relates to a containerized semi-solid mud packing sealing device for fluid equipment (hereinafter referred to as the device 10), which is used to seal a rotating shaft 12 passing through an orifice 27 of an equipment housing (hereinafter referred to as the housing 26) to prevent the fluid 11 in the housing 26 from leaking from the orifice 27. Figure 1 is a cross-sectional view of the device 10 before being assembled between the rotating shaft 12 and the housing 26, and Figure 2 1 is a cross-sectional view of the device 10 after being assembled between the rotating shaft 12 and the housing 26. The housing 26 can be the pump housing mentioned above, or can be the housing 26 of any other fluid device having the rotating shaft 12.

[0037] In this document, for ease of explanation, the structural details of the device 10 are described based on the fact that the device 10 has been assembled between the rotating shaft 12 and the housing 26, wherein the terms "front" and "rear" are defined along the axis L of the device 10, "front" means the side of the device 10 or the housing 26 axially close to the fluid 11 in the housing 26, and "rear" means the other side of the device 10 or the housing 26 axially away from the fluid 11 in the housing 26, and the terms "inside" and "outside" are defined perpendicular to the axis L of the device 10, "inside" means the side of the device 10 or the housing 26 radially close to the axis L of the device 10, and "outside" means the other side of the device 10 radially away from the axis L of the device 10.

[0038] Generally speaking, the device 10 includes a sleeve 14 mounted around a rotating shaft 12, a locking ring 16, a molded sealing ring assembly 17, a semi-solid mud filler 18, a cylindrical main gland 20, an annular secondary gland 22, a support frame 42, and one or more removable positioning blocks 34. Figure 1-Figure 2 、 Figure 4 、 Figure 8-Figure 9 and Figure 11 In order to clearly illustrate the filler 18, the support frame 42 is removed. Figure 6 In order to clearly illustrate the support frame 42, the filler 18 is removed.

[0039] The sleeve 14 is made of a hard material including any one of metal, ceramic, alloy, and silicon carbide, or a combination thereof.

[0040] like Figure 1 As shown, a locking ring 16 surrounds the rear end of the sleeve 14 to fasten the sleeve 14 to the rotating shaft 12. For example, one or more fastening screws can be screwed into one or more radially extending threaded holes 16a of the locking ring 16 and passed through the rear end of the sleeve 14, thereby fastening the sleeve 14 to the rotating shaft 12. As a result, when the rotating shaft 12 rotates, the sleeve 14 rotates along with the rotating shaft 12. Here, the diameter of the outer circumferential surface of the sleeve 14 remains substantially constant.

[0041] The inner peripheral surface of the front end of the sleeve 14 is formed with a sealing ring groove 15 for accommodating an elastic, for example, O-type sealing ring 19 (such as Figure 2 As shown), a seal is formed between the sleeve 14 and the rotating shaft 12.

[0042] like Figure 2 As shown, the front end of the main gland 20 forms a main gland cylinder 20a, and the rear end of the main gland 20 forms a main gland step 20b extending outward relative to the main gland cylinder 20a.

[0043] The main gland step 20b is configured to be fastened to the rear wall 26a around the orifice 27 of the housing 26 by means of one or more bolts 25, for example, via a sealing gasket 24 (for example, a gasket, or an elastic member made of fiber, rubber, etc.), so as to form a seal between the rear wall 26a of the housing 26 and the main gland step 20b, that is, the main gland 20. At the same time, the main gland cylinder 20a extends axially through the orifice 27 (such as Figure 1 As shown), it is preferred that the front wall surface 26b extends axially beyond the orifice 27 of the housing 26, thereby forming a gap 29 between the outer peripheral surface of the main gland cylinder 20a and the inner wall surface 26c of the housing 26 forming the orifice 27, allowing the fluid 11 to flow therein.

[0044] The outer contour of the main gland step 20b may have a circular shape (eg Figure 3As shown), any one of the shapes including waist shape, drum shape, square shape and wing shape to match the shape of the shell 26.

[0045] Continue to refer to Figure 1 and Figure 2 The rear end of the main gland cylinder 20a is connected to, for example, integrally formed with, the main gland step 20b. Optionally, a convex ring 20a1 is formed on the outer circumferential surface of the rear end of the main gland cylinder 20a. The convex ring 20a1 extends axially into the orifice 27 and terminates the gap 29. Compared to the axial length of the main gland cylinder 20a, the axial length of the convex ring 20a1 is significantly smaller than that of the main gland cylinder 20a, so that it can be ignored.

[0046] like Figure 2 As shown, the axial length X from the front end face of the first molded sealing ring 17a to the front end face of the main gland step 20b in the cylindrical space is more than twice the axial length Y from the rear end face of the second molded sealing ring 17b to the front end face of the main gland step 20b.

[0047] Continue to refer to Figure 1 and Figure 2 The inner circumference of the main gland cylinder 20a surrounds the outer circumference of the shaft sleeve 14 to form a cylindrical space, in which the molded sealing ring assembly 17 and the packing 18 are filled. Specifically, the front end of the main gland cylinder 20a forms an abutment step 20a2 extending inward relative to the inner circumference of the main gland cylinder 20a. A small gap is formed between the inner circumference of the abutment step 20a2 and the outer circumference of the shaft sleeve 14, so that the main gland cylinder 20a, i.e., the main gland 20, can be loosely fitted to the outer circumference of the shaft sleeve 14. For example, the front end surface of the abutment step 20a2 can be radially aligned with the front end surface of the shaft sleeve 14 to achieve a compact structure.

[0048] The molded seal ring assembly 17 includes a first molded seal ring 17 a and a second molded seal ring 17 b , and the filler 18 is located between the first molded seal ring 17 a and the second molded seal ring 17 b .

[0049] Here, the number of each of the first molded sealing ring 17 a and the second molded sealing ring 17 b is at least one.

[0050] Specifically, when the molded sealing ring assembly 17 includes multiple first molded sealing rings 17a, the multiple first molded sealing rings 17a are axially closely arranged side by side with each other. Similarly, when the molded sealing ring assembly 17 includes multiple second molded sealing rings 17b, the multiple second molded sealing rings 17b are axially closely arranged side by side with each other.

[0051] Here, each of the first molded sealing ring 17 a and the second molded sealing ring 17 b may be formed as a divisible component.

[0052] Specifically, at least one of the first molded sealing ring 17a and the second molded sealing ring 17b can be split into a first molded sealing ring component and a second molded sealing ring component along its axial cross section, so as to facilitate splicing the first molded sealing ring component and the second molded sealing ring component around the rotating shaft 12.

[0053] The rear end of the secondary gland 22 is fastened to the rear end face of the primary gland step 20b by means of a pre-tightening mechanism 28, so that the front end of the secondary gland 22 protrudes axially into the accommodation space and pushes against the second molded seal ring 17b. In other words, the front end face of the first molded seal ring 17a abuts the rear end face of the abutment step 20a2, the rear end face of the second molded seal ring 17b abuts the front end of the secondary gland 22, the outer circumference of the molded seal ring assembly 17 abuts the inner circumference of the primary gland cylinder 20a, and the inner circumference of the molded seal ring assembly 17 abuts the outer circumference of the shaft sleeve 14.

[0054] like Figure 4 As shown, the inner circumference of the secondary gland 22 is loosely fitted with the outer circumference of the shaft sleeve 14, while the inner circumference of the front end of the secondary gland 22 has a larger diameter than the inner circumference of the rear end of the secondary gland 22. Furthermore, the outer circumference of the front end of the secondary gland 22 has a smaller diameter than the inner circumference of the main gland step 20b, allowing the front end of the secondary gland 22 to smoothly protrude into the accommodating space as an axial protrusion. Consequently, the combined axial lengths of the molded seal ring assembly 17 and the packing 18 are no greater than the axial length of the cylindrical space, meaning that the second molded seal ring 17b does not extend axially beyond the rear end of the main gland step 20b.

[0055] The molded sealing ring assembly 17 may be a rope-like object woven from fibers (also known as packing), or may be made of rubber. The molded sealing ring assembly 17 has elastic-plastic properties and can be squeezed to elastic-plastic deformation.

[0056] The filler 18 may be made of a mixture of fibers and a lubricant, wherein the lubricant is a mixture of solid powder and oil.

[0057] Optionally, the main gland step 20b includes a through hole 23 extending from the outer circumferential surface of the main gland step 20b to the inner circumferential surface of the main gland step 20b to communicate with the cylindrical space. The axis of the through hole 23 forms an angle of, for example, greater than 60 degrees with the axis L of the device 10. A portion of the through hole 23 close to the outer circumferential surface of the main gland step 20b has a threaded joint 23a extending along the axis of the through hole 23. During normal operation of the device 10, the threaded joint 23a can be blocked by a nut 25. When it is necessary to add the filler 18, the nut 25 is removed to connect the interface of an external injector (e.g., a charging gun) to the threaded joint 23a, thereby injecting the filler 18 into the cylindrical space with the help of the external injector. The filler 18 helps to increase the sealing pressure formed in the cylindrical space so that the filler 18 is tightly compressed between the rear end face of the first molded sealing ring 17a and the front end face of the second molded sealing ring 17b.

[0058] Here, as Figure 5 As shown in detail, the preload mechanism 28 may include a bolt 30 having a head 30a and a screw, and a spring 32 sleeved on the bolt 30. When the bolt 30 passes through the axially extending through-hole 21 of the secondary gland 22 and is screwed into the axially extending threaded hole formed on the rear end surface of the primary gland step 20b, one end of the spring 32 abuts against the head 30a, and the other end of the spring 32 abuts against the rear end surface of the secondary gland 22 or the bottom of the groove 22a of the secondary gland 22. The preload force provided by the compression of the spring 32 secures the secondary gland 22 to the primary gland 20. At the same time, a certain gap is left between the front end surface of the rear end of the secondary gland 22, which does not protrude into the cylindrical space, and the rear end surface of the primary gland step 20b, to enable axial displacement of the secondary gland 22 relative to the primary gland 20. In other words, the diameter of the through-hole 21 of the secondary gland 22 is larger than the diameter of the screw and smaller than the diameter of the head 30a. The spring 32 may include a disc spring that provides greater force and a shorter stroke and a coil spring that provides less force and a longer stroke (e.g., Figure 5 Any one of the ones shown).

[0059] On the one hand, when the threaded joint 23a is sealed by the nut 25, the sealing pressure can be adjusted with the help of the pre-tightening mechanism 28. For example, if the bolt 30 is tightened, the pre-tightening force on the molded sealing ring assembly 17 and the packing 18 can be increased, while if the bolt 30 is loosened, the pre-tightening force on the molded sealing ring assembly 17 and the packing 18 can be reduced. In addition, the molded sealing ring assembly 17 and the packing 18 can be removed axially by removing the secondary gland 22 to replace the molded sealing ring assembly 17, and then the packing 18 can be injected into the cylindrical space through the through hole 23 using the external injector.

[0060] On the other hand, adding the spring 32 can alleviate the impact of shock and vibration on the secondary pressure cover 22 .

[0061] In particular, when the filler 18 is injected into the cylindrical space, the pressure in the cylindrical space suddenly increases to resist the preload force acting on the secondary gland 22, causing the secondary gland 22 to shift axially away from the main gland 20. When the pressure in the cylindrical space decreases, the secondary gland 22 can shift axially closer to the main gland 20. For example, during normal operation of the device 10, the molded seal ring assembly 17 may wear so that the total axial length of the molded seal ring assembly 17 and the filler 18 decreases. In this case, the secondary gland 22 can shift further axially closer to the main gland 20 until the gap is eliminated, that is, the front end surface of the secondary gland 22 is in contact with the rear end surface of the main gland 20, to compensate for the reduced total axial length of the molded seal ring assembly 17 and the filler 18.

[0062] like Figure 6 or return to Figure 2 and Figure 3 The locking ring 16 is rotatably positioned relative to the one or more positioning blocks 34, and the device 10 can be assembled together with the help of the one or more positioning blocks 34, that is, the sleeve 14, the locking ring 16, the molded sealing ring assembly 17, the packing 18, the main pressure cover 20 and the auxiliary pressure cover 22 are assembled together, so that the device 10 can be sleeved on the rotating shaft 12 in one step or the device 10 can be removed from the rotating shaft 12 in one step.

[0063] For example, the locking ring 16 can be axially positioned relative to the sleeve 14 by the one or more positioning blocks 34. Specifically, the positioning block 34 includes a first portion 34a and a second portion 34b that are angled (e.g., at a right angle), and one or more bolts 36 that extend axially through the first portion 34a of the positioning block 34 fasten the positioning block 34 to the rear end face of the secondary pressure cover 22. The axial length of the first portion 34a of the positioning block 34 is less than the axial length of the secondary pressure cover 22. In addition, the axial length of the first portion 34a of the positioning block 34 is equal to the distance between the rear end face of the secondary pressure cover 22 and the front end face of the locking ring 16. It can be seen that the secondary pressure cover 22 is adjacent to the locking ring 16 to achieve a compact structure.

[0064] The second portion 34b of the positioning block 34 includes a radial groove 34b1 that receives the outer peripheral edge of the locking ring 16. Alternatively, the outer peripheral edge of the locking ring 16 may form an outer peripheral annular guide groove, and the second portion 34b of the positioning block 34 includes a radial projection that is inserted into the outer peripheral annular guide groove of the locking ring 16. This restricts axial movement of the locking ring 16 relative to the shaft sleeve 14 while allowing rotation of the locking ring 16 relative to the shaft sleeve 14. After the device 10 with the positioning block 34 is mounted on the rotating shaft 12 in a single step, and before the rotating shaft 12 is rotated during operation of the fluid device, the positioning block 34 is removed from the shaft sleeve 14. When it is necessary to remove the device 10 from the rotating shaft 12, the positioning block 34 is reinstalled relative to the locking ring 16, and the one or more fastening screws are loosened to remove the device 10 from the rotating shaft 12 in a single step.

[0065] like Figure 6 As shown, the support skeleton 42 includes one or more axial struts 42c located between the first molded sealing ring 17a and the second molded sealing ring 17b, each axial strut 42c being suspended in the cylindrical space to increase the ability of the packing 18 to resist extrusion, such as preload, wherein, for details, reference may be made to Figure 7 The support frame 42 further includes a first annular support 42a that abuts the rear end face of the first molded sealing ring 17a, and a second annular support 42b that abuts the front end face of the second molded sealing ring 17b. The plurality of axial support rods 42c can be evenly distributed along the circumference of the first annular support 42a and the second annular support 42b and have elastic properties. Each axial support rod 42c is connected to the first annular support 42a and the second annular support 42b at both axial ends. For example, each axial support rod 42c includes a first distal end 42c1, a first stopper 42c2 extending relative to the first distal end 42c1, a second distal end 42c3, and a second stopper 42c4 extending relative to the second distal end 42c3. The first distal end 42c1 is slidably inserted into a corresponding opening of the first annular support 42a, and the second distal end 42c3 is slidably inserted into a corresponding opening of the second annular support 42b. Thus, the axial support rods 42c, suspended in the cylindrical space, enable the spacing between the first molded sealing ring 17a and the second molded sealing ring 17b to vary between a minimum spacing and a maximum spacing. When the spacing varies from the maximum spacing to the minimum spacing, the secondary gland 22 shifts axially forward until the first stopper 42c2 abuts against the first annular support 42a, and the second stopper 42c4 abuts against the second annular support 42b. When the spacing changes from the minimum spacing to the maximum spacing, the secondary gland 22 is displaced axially rearward until the spring 32 is fully compressed.

[0066] It can be seen that the support frame 42 of the present application can maintain a minimum spacing to resist shrinkage under external pressure, and at the same time solve the problem of overheating and expansion of the filler 18, or even seal burning loss, caused by the accumulation of internal pressure in the cylindrical space during online maintenance and pressurized replenishment of the filler 18.

[0067] In addition, the inner diameter of the first annular bracket 42a is larger than the inner diameter of the first molded sealing ring 17a (i.e., the diameter of the inner circumferential surface of the first molded sealing ring 17a), and the outer diameter of the first annular bracket 42a is smaller than the outer diameter of the first molded sealing ring 17a (i.e., the diameter of the outer circumferential surface of the first molded sealing ring 17a).

[0068] like Figure 8 As shown, when the positioning block 34 is removed from the sleeve 14 so that the sleeve 14 rotates with the rotating shaft 12, the filler 18 will be divided into a stationary portion 18a and a rotating portion 18b slidably engaged with / fitted with / contacting the stationary portion 18a, and the rotating portion 18b (for example, mostly composed of fibers in the filler 18) will be wound around the outer circumferential surface of the sleeve 14 or closer to the outer circumferential surface of the sleeve 14 to rotate with the sleeve 14, while the stationary portion 18a will fit onto or be closer to the inner circumferential surface of the main gland cylinder 20a, the rear end face of the first molded sealing ring 17a, and the front end face of the second molded sealing ring 17b to basically remain stationary.

[0069] Optionally, each axial support rod 42c may be closer to the inner circumference of the main gland cylinder 20a than the outer circumference of the sleeve 14, thereby avoiding the rotating portion 18b of the packing 18, so that the support skeleton 42 remains substantially stationary.

[0070] Therefore, during the rotation of the rotating shaft 12, the relative sliding between the stationary part 18a and the rotating part 18b will generate a large amount of heat. However, based on the fact that the axial length X from the front end face of the first molded sealing ring 17a to the front end face of the main pressure cover step 20b in the cylindrical space is more than twice the axial length Y from the rear end face of the second molded sealing ring 17b to the front end face of the main pressure cover step 20b, the fluid 11, especially the liquid, can circulate into the gap 29 to flow around the main part of the packing 18, thereby significantly cooling the packing 18.

[0071] Optionally, continue with reference to Figure 8The device 10 may further include an additional cylinder 20c integrally formed with the front end of the main gland cylinder 20a for chip removal. A spiral groove 38 is formed on the inner circumference of the additional cylinder 20c, wherein the direction of rotation of the spiral groove 38 is the same as the direction of rotation of the rotating shaft 12 (for example, clockwise). The spiral groove 38 extends along a helical line with a certain helix angle. The starting point of the spiral line is close to or on the front end surface of the additional cylinder 20c, and the end point of the spiral line is close to or on the rear end surface of the additional cylinder 20c. It can be understood that the rear end surface of the additional cylinder 20c coincides with the front end surface of the main gland cylinder 20a, that is, it abuts the front end surface of the step 20a2. The spiral groove 38 is separated from the cylindrical space.

[0072] Here, the radial groove depth (also referred to as groove diameter), the axial groove width and / or the groove cross-sectional area of ​​the spiral groove 38 remain constant or gradually increase from the starting point to the end point of the spiral line.

[0073] In general, the radial groove depth of the spiral groove 38 refers to the radial depth from the groove top 38a (smaller diameter) to the groove bottom 38b (larger diameter) of the spiral groove 38. The axial groove width of the spiral groove 38 refers to the axial width of the spiral groove 38 measured on a reference line parallel to the axis of the spiral groove 38. The groove cross-sectional area of ​​the spiral groove 38 is calculated based on at least the radial groove depth in an axial cross-section of the spiral groove 38.

[0074] For example, Figure 8 As shown in FIG. 1 , when the radial groove depth of the spiral groove 38 gradually increases, the diameter of the groove bottom 38b of the spiral groove 38 gradually increases from the starting point to the end point of the spiral line, while the diameter of the groove top 38a of the spiral groove 38 can remain substantially constant. In this case, the diameter of the groove top 38a of the spiral groove 38 can be smaller than the outer diameter of the sleeve 14 (i.e., the diameter of the outer circumferential surface of the sleeve 14) and larger than the inner diameter of the sleeve 14 (i.e., the diameter of the inner circumferential surface of the sleeve 14).

[0075] For example, Figure 9 As shown in FIG. 1 , when the radial groove depth of the spiral groove 38 gradually increases, the diameter of the groove top 38 a of the spiral groove 38 gradually increases from the starting point to the end point of the spiral line, while the diameter of the groove bottom 38 b of the spiral groove 38 can remain substantially constant. In this case, the minimum diameter of the groove top 38 a of the spiral groove 38 will be greater than the outer diameter of the sleeve 14.

[0076] During the rotation of the rotating shaft 12 , the spiral groove 38 remains stationary and cooperates with the rotating shaft 12 to prevent the fluid 11 , especially particulate impurities in the liquid, from entering the cylindrical space to damage the seal between the sleeve 14 and the main gland 20 .

[0077] Optionally, refer to Figure 10The front end surface of the additional cylinder 20c is formed with a plurality of grooves 20c1 or protruding teeth 20c2 arranged at intervals and optionally at equal distances. Each groove 20c1 or protruding tooth 20c2 passes through and / or extends from the outer circumference of the additional cylinder 20c to the inner circumference of the additional cylinder 20c, and each groove 20c1 or protruding tooth 20c2 is separated from the cylindrical space. Each groove 20c1 or protruding tooth 20c2 can be straight (e.g., on the axis of the additional cylinder 20c (coinciding with the axis L of the device 10)). Figure 10 as shown), tilted at a certain angle relative to the axis of the additional cylinder 20c, and / or spirally around the axis of the additional cylinder 20c.

[0078] Optionally, refer to Figure 11 The device 10 includes an additional sleeve 14a integrally formed with the front end of the sleeve 14 for chip removal. The outer circumference of the additional sleeve 14a is formed with a plurality of axially spaced pumping gear rings 40, which are separated from the cylindrical space. For example, each pumping gear ring 40 may have straight, helical, or spiral teeth, or a combination thereof.

[0079] Optionally, refer to Figure 12 The front end surface of the additional sleeve 14a is formed with a plurality of grooves 14a1 or protruding teeth 14a2 arranged at intervals and optionally at equal distances. Each groove 14a1 or protruding tooth 14a2 passes through and / or extends from the outer circumference of the additional sleeve 14a to the inner circumference of the additional sleeve 14a, and each groove 14a1 or protruding tooth 14a2 is separated from the cylindrical space. Each groove 14a1 or protruding tooth 14a2 can be straight (e.g., on the axis of the additional sleeve 14a (coinciding with the axis L of the device 10)). Figure 12 As shown), it is inclined at a certain angle relative to the axis of the additional sleeve 14a, and / or is spiral around the axis of the additional sleeve 14a.

[0080] During the rotation of the rotating shaft 12 , the sleeve 14 and thus the pump gear ring 40 rotate along with the rotating shaft 12 to prevent particles in the fluid 11 from entering the cylindrical space and damaging the seal between the sleeve 14 and the main gland 20 .

[0081] Back to Figure 9 When the proportion of particulate impurities in the fluid 11 is large, an additional cylinder 20c and an additional sleeve 14a can be provided simultaneously, wherein the spiral groove 38 of the additional cylinder 20c faces the pumping gear ring 40 of the additional sleeve 14a in a radially spaced manner. Figure 9In the embodiment, the axial length of the additional cylinder 20c is equal to the axial length of the additional sleeve 14a, but this is not necessary. It will be understood that the various features provided above regarding the additional cylinder 20c and the additional sleeve 14a can be flexibly combined or implemented separately. Although some specific embodiments of the present application have been described in detail through examples, those skilled in the art will understand that the above examples are for illustration only and are not intended to limit the scope of the present application. Those skilled in the art will understand that the devices in the above embodiments may be modified without departing from the scope and spirit of the present application. The scope of the present application is defined by the appended claims.

Claims

1. A containerized semi-solid mud packing sealing device (10) for fluid equipment, used for sealing a rotating shaft (12) passing through an orifice (27) of an equipment housing (26) to prevent a fluid (11) in the equipment housing (26) from leaking from the orifice (27), characterized in that: The sealing device (10) comprises a shaft sleeve (14) installed around a rotating shaft (12), a locking ring (16), a molded sealing ring assembly (17), a semi-solid mud filler (18), a cylindrical main gland (20), and an annular secondary gland (22), wherein: The front end of the main gland (20) forms a main gland cylinder (20a), and the rear end of the main gland (20) forms a main gland step (20b) extending outward relative to the main gland cylinder (20a); The main gland step (20b) is configured to be fastened to a rear wall surface (26a) of the device housing (26) around the orifice (27), while the main gland cylinder (20a) passes through the orifice (27), thereby forming a gap (29) between the outer peripheral surface of the main gland cylinder (20a) and the inner wall surface (26c) of the device housing (26) forming the orifice (27), allowing the fluid (11) to flow therein; The inner circumference of the main gland cylinder (20a) surrounds the outer circumference of the shaft sleeve (14) to form a cylindrical space, the molded sealing ring assembly (17) and the filler (18) are filled in the cylindrical space, and the filler (18) can flow in the cylindrical space; The main gland step (20b) includes a through hole extending from the outer circumferential surface of the main gland step (20b) to the inner circumferential surface of the main gland step (20b) to communicate with the cylindrical space, and a portion of the through hole close to the outer circumferential surface of the main gland step (20b) has a threaded joint (23a), and the threaded joint (23a) is suitable for connecting to an interface of an external injector or being blocked; The molded sealing ring assembly (17) includes a first molded sealing ring (17a) and a second molded sealing ring (17b), and the filler (18) is located between the first molded sealing ring (17a) and the second molded sealing ring (17b); The auxiliary gland (22) is fastened to the rear end face of the main gland step (20b) by means of a pre-tightening mechanism (28), so that the front end of the auxiliary gland (22) protrudes axially forward from the rear wall (26a) of the main gland step (20b) into the accommodation space and pushes against the second molded sealing ring (17b); and The locking ring (16) surrounds the rear end of the sleeve (14) and secures the sleeve (14) to the rotating shaft (12).

2. The sealing device (10) according to claim 1, characterized in that The axial length (X) from the front end face of the first molded sealing ring (17a) to the front end face of the main pressure cover step (20b) in the cylindrical space is more than twice the axial length (Y) from the rear end face of the second molded sealing ring (17b) to the front end face of the main pressure cover step (20b).

3. The sealing device (10) according to claim 1, characterized in that The sealing device (10) further comprises an additional cylinder (20c) integrally formed with the front end of the main gland cylinder (20a), wherein the inner circumferential surface of the additional cylinder (20c) forms a spiral groove (38), or wherein the front end surface of the additional cylinder (20c) forms a plurality of grooves extending from the outer circumferential surface of the additional cylinder (20c) to the inner circumferential surface of the additional cylinder (20c) and arranged at intervals; and / or The sealing device (10) further comprises an additional sleeve (14a) integrally formed with the front end of the sleeve (14), wherein the outer peripheral surface of the additional sleeve (14a) forms a plurality of toothed rings arranged axially at intervals, or wherein the front end surface of the additional sleeve (14a) forms a plurality of grooves extending from the outer peripheral surface of the additional sleeve (14a) to the inner peripheral surface of the additional cylinder (20c) and arranged at intervals.

4. The sealing device (10) according to claim 3, characterized in that The starting point of the spiral groove (38) is close to or located at the front end surface of the additional cylinder (20c), and the end point of the spiral groove (38) is close to or located at the rear end surface of the additional cylinder (20c) and is separated from the cylindrical space, and the radial groove depth, axial groove width and / or groove cross-sectional area of ​​the spiral groove (38) remain constant or gradually increase from the starting point to the end point of the spiral groove (38).

5. The sealing device (10) according to claim 3, characterized in that The plurality of tooth rings are separated from the cylindrical space, and each tooth ring is in any one of a straight tooth shape, a helical tooth shape or a spiral tooth shape or a combination thereof.

6. The sealing device (10) according to claim 1, characterized in that It also includes a support skeleton (42), which includes one or more axial struts (42c) located between the first molded sealing ring (17a) and the second molded sealing ring (17b), each axial strut (42c) being suspended in the cylindrical space, and the one or more axial struts (42c) are configured so that the spacing between the first molded sealing ring (17a) and the second molded sealing ring (17b) can be changed between a minimum spacing and a maximum spacing.

7. The sealing device (10) according to claim 6, characterized in that The support skeleton (42) also includes a first annular bracket (42a) abutting against the rear end face of the first molded sealing ring (17a) and a second annular bracket (42b) abutting against the front end face of the second molded sealing ring (17b), and each axial support rod (42c) includes a first tip (42c1), a first limiting portion (42c2) protruding relative to the first tip (42c1), a second tip (42c3) and a second limiting portion (42c4) protruding relative to the second tip (42c3), the first tip (42c1) being slidably inserted into the first annular bracket (42a), and the second tip (42c3) being slidably inserted into the second annular bracket (42b), so that at the minimum spacing, the first limiting portion (42c2) abuts against the first annular bracket (42a), and the second limiting portion (42c4) abuts against the second annular bracket (42b).

8. The sealing device (10) according to claim 7, characterized in that The pre-tightening mechanism (28) includes a bolt and a spring (32) sleeved on the bolt. The bolt passes through an axially extending through hole of the auxiliary pressure cover (22) and is screwed into a threaded hole formed on the rear end face of the main pressure cover step (20b). The auxiliary pressure cover (22) is fastened to the main pressure cover (20) by the pre-tightening force provided by the compression of the spring (32). At the same time, a certain gap is left between the front end face of the rear end of the auxiliary pressure cover (22) that does not protrude into the cylindrical space and the rear end face of the main pressure cover step (20b), so that the auxiliary pressure cover (22) can be axially displaced relative to the main pressure cover (20), and at the maximum spacing, the spring (32) is completely compressed.

9. The sealing device (10) according to claim 1, characterized in that It also includes one or more detachable positioning blocks (34), which are configured to connect the locking ring (16) to the auxiliary pressure cover (22) to assemble the sealing device (10) together, so that the sealing device (10) can be sleeved on the rotating shaft (12) or the sealing device (10) can be removed from the rotating shaft (12) in one step, and the one or more positioning blocks (34) are configured to be removed from the locking ring (16) and the auxiliary pressure cover (22) so that the locking ring (16) and the sleeve (14) can rotate together with the rotating shaft (12) during operation of the fluid device.

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