Indirectly cooled seal assembly, low speed rotor pump, cam pump, centrifugal pump seal assembly

Abstract

The utility model discloses an indirect cooling sealing assembly, low -speed rotor pump, cam pump, centrifugal pump sealing assembly relates to mechanical seal technical field, solve the problem that low -speed pump does not need complex cooling structure, need to give consideration to economy and sealing life. The component includes shaft sleeve, and the shaft sleeve is equipped with press component, gland, static ring, dynamic ring, dynamic ring seat, spring from left to right in proper order, and the gland is equipped with liquid inlet hole, liquid outlet hole and the steel cover with cooling cavity, and the cooling cavity links liquid inlet hole and liquid outlet hole, and the steel cover is fixed with static ring through static ring pin, and dynamic ring seat is connected with the shaft sleeve axial movable slot through dynamic ring pin, and the spring is arranged in the spring groove of shaft sleeve to compensate dynamic static ring wear, and the first sealing ring is equipped between the shaft sleeve, dynamic ring seat and dynamic ring, and the second sealing ring is equipped between the steel cover and static ring, and the press component is opened with pump body assembly hole. The utility model discloses simple structure, low in cost can prolong the sealing life, and is suitable for low -speed pump use.

Description

Technical Field

[0001] This utility model relates to the field of mechanical seal technology, and in particular to an indirect cooling sealing assembly, a rotary pump, a cam pump, and a centrifugal pump sealing assembly. Background Technology

[0002] In the food processing industry, the higher the pump speed, the more severe the wear on the end faces of the dynamic and stationary rings of the mechanical seal configured with the pump's output. To reduce end face wear, the mainstream solution is to incorporate heat dissipation measures for the dynamic and stationary rings to extend the service life of the mechanical seal. The preferred approach is to create a cooling sealing cavity between the dynamic and stationary rings, where the coolant directly contacts the rings to remove heat. However, this cooling structure is complex. For example, Chinese patent application number 2024231880632 discloses a mechanical seal with a liquid-cooled sealing cavity. The sealing end faces of the dynamic and stationary rings, the bushing, the packing, the main pressure plate, the stationary ring seal, and the rotating ring seal, along with the stationary ring itself, all work together to form the cooling sealing cavity. The main pressure plate has inlet and outlet pipes respectively connecting to the cooling sealing cavity. Its main drawback is the complexity of the cooling structure and the high processing cost. However, for low-speed pumps, the heat generated by the dynamic and stationary rings is small, making a complex cooling structure unnecessary. While considering extending the service life of the mechanical seal through reasonable cooling methods, greater emphasis should be placed on economic efficiency to save on procurement costs.

[0003] Therefore, it is of great significance to propose an indirect cooling sealing assembly that is simple in structure, low in cost, and can also extend service life, as well as a sealing assembly for low-speed rotor pumps, cam pumps, and centrifugal pumps. Utility Model Content

[0004] The purpose of this invention is to overcome the shortcomings of the prior art and provide an indirect cooling sealing component, rotor pump, and cam pump sealing component that takes into account the heat dissipation requirements of low-speed pumps and economy, and extends the life of sealing components.

[0005] The above-mentioned objectives of this utility model are achieved through the following technical means: An indirect cooling sealing assembly includes a bushing 1, characterized in that the bushing 1 is provided from left to right with: a pressing assembly 2, a pressure cap 3, a stationary ring 4, a rotating ring 5, a rotating ring seat 6, and a spring 7. One end of the pressure cap 3 is provided with a liquid inlet 31, and the other end is provided with a liquid outlet 32; The pressure cap 3 also includes a steel sleeve 33, which has a cooling cavity 34 that connects the liquid inlet 31 and the liquid outlet 32. The steel sleeve 33 is fixed to the stationary ring 4 by a number of stationary ring pins 41; The bushing 1 has several axial movable grooves 11. The movable ring 5 is connected to the movable ring seat 6. The movable ring seat 6 is movably connected to the movable grooves 11 through several movable ring pins 51. The number of movable ring pins 51 matches the number of movable grooves 11. The stationary ring 4 is sealed to the end face of the movable ring 5. The bushing 1 also has a one-way limiting spring groove 12, and the spring groove 12 is provided with the spring 7 for axial compensation of the wear of the end faces of the stationary ring 4 and the moving ring 5. A first sealing ring 91 is provided between the bushing 1, the rotating ring seat 6 and the rotating ring 5, and a second sealing ring 92 is provided between the steel sleeve 33 and the stationary ring 4. The pressing component 2 has a pump body assembly hole 8.

[0006] Preferably, the pressing assembly 2 includes a locking ring 21 and a pre-fixing block 22 disposed on the locking ring 21 and pressing the steel sleeve 33; Both the locking ring 21 and the pre-fixing block 22 have several mutually cooperating screw holes. The pre-fixing block 22 is pre-fixed to the locking ring 21 by screws to press the steel sleeve 33. The screw hole of the locking ring 21 corresponds to the pump body assembly hole 8.

[0007] Furthermore, the steel sleeve 33 extends to one side with a pressing ring 331, which presses the stationary ring 4, and the second sealing ring 92 is disposed between the pressing ring 331 and the stationary ring 4 of the steel sleeve 33.

[0008] Furthermore, the stationary ring 4 has a "convex" cross-section, with its upper side abutting against the pressing ring 331. Its left side is fixed to the steel sleeve 33 by the stationary ring pin 41, and its right side forms a right-angle protrusion to the right, which is the stationary ring redundant wear part 42 and seals the end face of the moving ring 5.

[0009] Furthermore, the cross-section of the moving ring seat 6 is T-shaped, with a right-angled gap 61 on its left side connected to the moving ring 5. A portion of the moving ring 5 protrudes from the moving ring seat 6 to form a moving ring redundant wear portion 52 that seals the end face of the stationary ring redundant wear portion 42. Its lower side abuts against the bushing 1, and its right side is movably connected to the movable groove 11 through the moving ring pin 51. Its right end face abuts against the spring 7.

[0010] Preferably, the first sealing ring 91 is disposed between the bushing 1, the lower left side of the rotating ring seat 6, and the rotating ring 5.

[0011] Preferably, one end of the bushing 1 is provided with a third sealing ring 93 to prevent the medium from overflowing.

[0012] The present utility model also discloses a sealing assembly for a low-speed rotor pump. The indirect cooling sealing assembly is assembled on the rotor pump. The indirect cooling sealing assembly is assembled on the pump body of the rotor pump by screws through the pump body assembly hole 8, and the shaft sleeve 1 is assembled on the pump shaft of the rotor pump.

[0013] The present utility model also discloses a sealing assembly for a low-speed cam pump. The indirect cooling sealing assembly is assembled on the cam pump. The indirect cooling sealing assembly is assembled on the pump body of the cam pump by screws through the pump body assembly hole 8, and the shaft sleeve 1 is assembled on the pump shaft of the cam pump.

[0014] The present utility model also discloses a sealing assembly for a low-speed centrifugal pump. The indirect cooling sealing assembly is assembled on the centrifugal pump. The indirect cooling sealing assembly is assembled on the pump body of the centrifugal pump by screws through the pump body assembly hole 8, and the shaft sleeve 1 is assembled on the pump shaft of the centrifugal pump.

[0015] The beneficial effects of adopting the above technical solutions are as follows: 1). By integrating the cooling cavity in the steel sleeve, the cooling structure is simplified. The spring realizes axial compensation for wear, and the double sealing rings prevent leakage, taking into account the heat dissipation requirements and economy of the low-speed pump, and extending the service life of the sealing assembly.

[0016] 2). The "locking ring + pre-fixed block" structure improves the fixing stability of the steel sleeve. The design of aligning the screw holes simplifies the assembly positioning, reduces the assembly error, and lowers the operation difficulty.

[0017] 3). The pressing ring of the steel sleeve stably axially positions the stationary ring. The second sealing ring is arranged between the pressing ring and the stationary ring, which not only enhances the sealing to prevent coolant leakage but also reduces the aging of the sealing ring.

[0018] 4). The "convex"-shaped stationary ring is adapted to the pressing ring of the steel sleeve and the moving ring. The redundant wear part of the stationary ring reserves a wear allowance, so there is no need to frequently replace the stationary ring, and its service life is extended.

[0019] 5). The "T"-shaped moving ring seat stably fixes the moving ring. The redundant wear part of the moving ring cooperates with the redundant part of the stationary ring, synchronously consuming the wear amount, and配合 with the spring compensation, extending the overall service life of the sealing assembly.

[0020] 6). The first sealing ring is arranged between the shaft sleeve, the lower left side of the moving ring seat and the moving ring, accurately sealing the gaps among the three, and further blocking the leakage path of the medium.

[0021] 7). A third sealing ring is arranged inside the shaft sleeve, effectively blocking the overflow of the medium in the pump from the gap between the shaft sleeve and the pump shaft, and avoiding polluting the internal components of the assembly and the operating environment.

[0022] 8). The indirect cooling sealing assembly is adapted to the low-speed rotor pump, and is firmly assembled through the pump body assembly hole and the shaft sleeve, preventing the overflow of viscous media, and meeting the requirements of scenarios such as food processing.

[0023] 9) The components are compatible with low-speed cam pumps, and spring compensation offsets the impact of pressure fluctuations on the sealing end face. Indirect cooling avoids coolant contamination of the medium, ensuring clean delivery.

[0024] 10) The components are compatible with low-speed centrifugal pumps, with double sealing rings to prevent leakage, cooling chambers to dissipate heat and prevent end-area heat, and simplified structure to reduce centrifugal pump maintenance costs and assembly difficulty. Attached Figure Description

[0025] Figure 1 This is a side cross-sectional view of the indirect cooling sealing assembly; Figure 2 This is a side view of the indirect cooling sealing assembly. Figure 3 yes Figure 1 A magnified view of part A.

[0026] Among them, there are: bushing 1; axial movable groove 11; spring groove 12; pressing assembly 2; locking ring 21; pre-fixing block 22; pressure cap 3; liquid inlet hole 31; liquid outlet hole 32; steel sleeve 33; pressing ring 331; cooling chamber 34; stationary ring 4; stationary ring pin 41; stationary ring redundant wear part 42; moving ring 5; moving ring pin 51; moving ring redundant wear part 52; moving ring seat 6; right angle missing part 61; spring 7; pump body assembly hole 8; first sealing ring 91; second sealing ring 92; third sealing ring 93. Detailed Implementation

[0027] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only a part of the embodiments of the present utility model, and not all of them. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of the present utility model.

[0028] Example 1. This example addresses the need in the background art for low-speed pumps to operate without complex cooling structures while balancing economy and seal life. It provides a simple, low-cost indirect cooling sealing assembly, such as... Figure 1-3 As shown, the specific structure is as follows: The indirect cooling sealing assembly includes a bushing 1, which is fitted with a pressing assembly 2, a pressure cap 3, a stationary ring 4, a rotating ring 5, a rotating ring seat 6, and a spring 7 from left to right. The connection and structural design of each component are as follows: One end of the pressure cap 3 has an inlet hole 31 and the other end has an outlet hole 32. The pressure cap 3 also integrates a steel sleeve 33. The steel sleeve 33 has a cooling cavity 34 machined inside. The two ends of the cooling cavity 34 are connected to the inlet hole 31 and the outlet hole 32 respectively, forming a coolant flow channel. Heat dissipation can be achieved without additional complex piping, reducing structural complexity and processing costs.

[0029] The steel sleeve 33 and the stationary ring 4 are fixedly connected by several stationary ring pins 41 to ensure that the stationary ring 4 remains relatively stable with the steel sleeve 33 during operation, and to avoid displacement affecting the sealing effect.

[0030] The side wall of the bushing 1 has several axial movable grooves 11. The moving ring 5 is fixedly connected to the left side of the moving ring seat 6. The moving ring seat 6 is movably connected to the axial movable grooves 11 through several moving ring pins 51, and the number of moving ring pins 51 is completely matched with the number of axial movable grooves 11. This design allows the moving ring seat 6 to drive the moving ring 5 to move axially along the axial movable grooves 11, while ensuring that the end faces of the stationary ring 4 and the moving ring 5 always remain in contact and sealed, meeting the sealing requirements of low-speed pumps.

[0031] The outer wall of the bushing 1 is also provided with a one-way limiting spring groove 12. The spring 7 is installed in the spring groove 12, and the left end of the spring 7 abuts against the right end face of the moving ring seat 6. When the sealing end faces of the stationary ring 4 and the moving ring 5 are worn due to long-term use, the spring 7 can push the moving ring seat 6 to move to the left along the axial movable groove 11 through its own elastic force, and drive the moving ring 5 to move to the left synchronously, so as to realize axial compensation for the wear of the end face and extend the overall service life of the sealing assembly.

[0032] To further improve sealing performance and prevent media leakage, a first sealing ring 91 is provided at the contact position of the bushing 1, the rotating ring seat 6, and the rotating ring 5; a second sealing ring 92 is provided at the contact position of the steel sleeve 33 and the stationary ring 4. The double sealing design ensures sealing reliability, and the installation position of the sealing ring does not require additional complex structure, thus balancing sealing effect and cost control.

[0033] The pressing component 2 has a pump body mounting hole 8, which is used to connect and fix the entire indirect cooling sealing component to the external pump body. During subsequent assembly, the component and the pump body can be fixed by simply passing screws through the pump body mounting hole 8, which simplifies the assembly process.

[0034] Indirect cooling principle The core of the "indirect cooling" of this component lies in the fact that the coolant does not directly contact the sealing end faces of the dynamic ring 5 and the stationary ring 4, but instead uses the steel sleeve 33 as an intermediate heat carrier. The steel sleeve has good thermal conductivity and economy, and indirectly absorbs and carries away the heat generated by the sealing end faces. The specific process is as follows: Heat generation: When the pump is working at low speed, the moving ring 5 rotates with the pump shaft, while the stationary ring 4 remains stationary. The sealing end faces of the two generate heat due to relative friction. Because the pump speed is low, the total heat generation is small, and the heat dissipation needs can be met without direct cooling.

[0035] Heat transfer: The stationary ring 4 is fixedly connected to the steel sleeve 33 through the stationary ring pin 41. The heat generated by the friction of the rotating ring 5 is transferred to the stationary ring 4 through the fitted sealing end face, and then conducted to the steel sleeve 33 by the stationary ring 4. At the same time, the heat of the rotating ring 5 itself is also indirectly transferred to the bushing 1 through the rotating ring seat 6, and some of the heat is further conducted to the steel sleeve 33, making the steel sleeve 33 a heat concentration carrier.

[0036] Coolant heat dissipation: External coolant flows in from the inlet hole 31 of the pressure cap 3 and enters the cooling chamber 34 inside the steel sleeve 33; the coolant fully contacts the inner wall of the steel sleeve 33 in the cooling chamber 34, absorbs the heat accumulated in the steel sleeve 33, and the coolant with increased temperature flows out of the component from the outlet hole 32, completing the heat transfer.

[0037] Circulating cooling: By continuously inputting low-temperature coolant and discharging high-temperature coolant, a stable circulating heat dissipation system is formed, which keeps the temperature of the steel sleeve 33 at a low level, thereby continuously removing the heat from the sealing end faces of the dynamic ring 5 and the stationary ring 4, avoiding accelerated wear of the end faces due to overheating, and ultimately achieving the dual goals of "simplifying the structure and extending the sealing life", which is fully adapted to the economic and practical needs of low-speed pumps in the background technology.

[0038] The indirect cooling sealing assembly of this embodiment simplifies the heat dissipation structure by integrating the cooling chamber 34 into the steel sleeve 33. Combined with the axial compensation function of the spring 7 and the sealing design of the sealing ring, it not only meets the heat dissipation and sealing requirements of the low-speed pump, but also greatly reduces the structural complexity and processing and procurement costs, making it perfectly suited for the application scenarios of low-speed pumps.

[0039] Example 2. This example further illustrates the pressing component based on Example 1, such as... Figure 1 As shown, the pressing assembly 2 includes a locking ring 21 and a pre-fixing block 22 disposed on the locking ring 21 and pressing the steel sleeve 33; Both the locking ring 21 and the pre-fixing block 22 have several mutually cooperating screw holes. The pre-fixing block 22 is pre-fixed to the locking ring 21 by screws to press the steel sleeve 33. The screw hole of the locking ring 21 corresponds to the pump body assembly hole 8.

[0040] In this embodiment, the pressing component 2 has a double-layer structure, with the core including a locking ring 21 and a pre-fixing block 22. The two work together to achieve stable pressing and precise positioning of the steel sleeve 33. The connection and functional design of each component are as follows: The basic positioning function of the locking ring: The locking ring 21 is a ring structure, which is sleeved on the outside of the bushing 1. Its inner side fits against the outer wall of the bushing 1, and plays a basic radial positioning role. The side wall of the locking ring 21 has several screw holes. The position and diameter of these screw holes match the subsequent pump body assembly requirements, and a positioning reference is reserved for the connection between the component and the pump body.

[0041] Pre-fixing block pressing and pre-positioning: The number of pre-fixing blocks 22 matches the number of screw holes in the locking ring, fitting snugly against the outer wall of the locking ring 21; the pre-fixing blocks 22 also have several screw holes, which are perfectly aligned with the screw holes in the locking ring 21. During assembly, screws are passed through the aligned screw holes of the pre-fixing blocks 22 and the locking ring 21 to pre-fix the pre-fixing blocks 22 onto the locking ring 21. At this time, the inner side of the pre-fixing blocks 22 will tightly abut against the outer wall of the steel sleeve 33, forming a uniform radial pressing force on the steel sleeve 33 to fix the gland. After this sealing assembly is assembled on the pump shaft, the pre-fixing component can be removed or not (whether it is removed depends on the accessories configured for the pump) to fix this sealing assembly to the pump. If the pre-fixing component is removed, the pump accessories take over the pressing of the steel sleeve.

[0042] This embodiment solves the potential offset problem that may occur when the steel sleeve is positioned solely by the bushing by using a combination structure of "locking ring + pre-fixing block". Furthermore, the overall structure has no complex parts, and the processing and assembly costs are controllable, further enhancing the practicality and economy of the indirect cooling sealing assembly in low-speed pump scenarios.

[0043] Example 3. This example is based on Example 1, and further illustrates the steel sleeve, such as... Figure 1 and Figure 3 As shown, the steel sleeve 33 extends to one side with a pressing ring 331, which presses the stationary ring 4. The second sealing ring 92 is disposed between the pressing ring 331 and the stationary ring 4 of the steel sleeve 33.

[0044] This embodiment focuses on the structural improvement of the steel sleeve 33, providing a stable axial positioning and sealing foundation for the stationary ring 4. On the side of the steel sleeve 33 facing the stationary ring 4, an integrally formed annular pressing ring 331 extends outward. The inner diameter of the pressing ring 331 matches the outer diameter of the stationary ring 4. During assembly, the end face of the pressing ring 331 will tightly abut against the left end face of the stationary ring 4, forming an axial pressing force on the stationary ring 4. This prevents the stationary ring 4 from axially displacing due to coolant flow or pump body vibration during operation, ensuring that the sealing end faces of the stationary ring 4 and the moving ring 5 are always in contact.

[0045] The second sealing ring position is optimized: the second sealing ring 92 is set between the contact end face of the pressing ring 331 of the steel sleeve 33 and the stationary ring 4; this position can utilize the pressing force of the pressing ring 331 to enhance the sealing effect of the sealing ring, prevent the medium from overflowing, and the second sealing ring does not come into contact with the coolant, reducing the aging and wear of the sealing ring.

[0046] Example 4. This example, based on Example 3, further illustrates the fit between the stationary ring, the steel sleeve, and the rotating ring, such as... Figure 1 and Figure 3 As shown, the stationary ring 4 has a "convex" cross-section, with its upper side abutting against the pressing ring 331. Its left side is fixed to the steel sleeve 33 by the stationary ring pin 41, and its right side forms a right-angle protrusion to the right, which is the stationary ring redundant wear part 42 and seals the end face of the moving ring 5.

[0047] In this embodiment, the cross-section of the stationary ring 4 is convex, divided into a right "protrusion" and a left "base", which are integrally formed, taking into account both structural strength and ease of processing.

[0048] The engagement with the steel sleeve: The upper end face of the left base of the stationary ring 4 closely abuts against the end face of the pressing ring 331 of the steel sleeve 33 in embodiment 3, and the axial displacement of the stationary ring 4 is restricted by the axial pressure of the pressing ring 331; at the corresponding position of the left base of the stationary ring 4 and the steel sleeve 33, several stationary ring pins 41 are used to fix it through, further restricting the radial rotation of the stationary ring 4, ensuring that the stationary ring 4 and the steel sleeve 33 are completely synchronously positioned, and avoiding relative displacement that could damage the sealing surface.

[0049] Redundant design of sealing end face: The right side "protrusion" of stationary ring 4 is a right-angled ring structure, defined as the stationary ring redundant wear part 42; the end face of the protrusion fits with the end face of the rotating ring 5 to form a sealing surface, and the axial length of the protrusion is reserved with a certain wear margin. Even if the rear end face wears after long-term use, as long as the redundant length is not exhausted, there is no need to replace stationary ring 4 immediately, which greatly extends the service life of stationary ring, reduces maintenance costs, and meets the "low cost and low maintenance" requirements of low speed pumps.

[0050] Example 5. This example, based on Example 3, further illustrates the fit between the rotating ring, the rotating ring seat, the stationary ring, and the steel sleeve, as follows: Figure 1 and Figure 3 As shown, the cross-section of the moving ring seat 6 is "T" shaped, with a right-angled gap 61 on its left side connected to the moving ring 5. A portion of the moving ring 5 protrudes from the moving ring seat 6 to form a moving ring redundant wear portion 52 that seals the end face of the stationary ring redundant wear portion 42. Its lower side abuts against the bushing 1, and its right side is movably connected to the movable groove 11 through the moving ring pin 51. Its right end face abuts against the spring 7.

[0051] This embodiment is based on the "convex" shaped stationary ring of embodiment 4, and designs a "T" shaped moving ring seat 6 and a moving ring 5 with redundant wear parts to achieve sealing adaptation with the stationary ring 4 and compensation coordination with the spring 7: The moving ring seat has a "T"-shaped structure: the cross-section of the moving ring seat 6 is "T"-shaped, divided into a left "connecting part" and a right "support part", with a simple and high-strength overall structure. The left connecting part has an inwardly recessed right-angled notch 61. The shape and size of this notch 61 perfectly match the outer contour of the moving ring 5. The moving ring 5 is fixed within the notch 61, ensuring that the moving ring 5 and the moving ring seat 6 move axially synchronously, preventing the moving ring 5 from falling off or shifting.

[0052] Right side support: The lower end face closely abuts against the outer wall of the bushing 1, which plays a radial positioning role; the right end face directly abuts against the spring 7. When the spring 7 generates axial elastic force, it can directly push the moving ring seat 6 to drive the moving ring 5 to move to the left, thereby achieving wear compensation.

[0053] The rotating ring redundant wear section design: After the rotating ring 5 is fixed to the empty part 61 of the rotating ring seat 6, a portion protrudes from the left end face of the rotating ring seat 6. This protruding portion is defined as the rotating ring redundant wear section 52. The axial length of the rotating ring redundant wear section 52 matches the length of the stationary ring redundant wear section 42 in embodiment 4, and the end faces of the two fit together to form a complete sealing surface. When the sealing surface wears due to friction, the redundant sections on both sides can be consumed simultaneously, ensuring that the sealing effect is not interrupted, and at the same time extending the overall replacement cycle of the rotating ring and the stationary ring. Replacement is performed when the wear continues until the left end face of the rotating ring seat abuts against the right end face of the stationary ring.

[0054] The moving ring seat 6 is connected to the axial moving groove 11 of the bushing 1 by a number of moving ring pins 51 on the right side support. This design allows the moving ring seat 6 to move stably to the left along the axial moving groove 11 under the push of the spring 7, avoiding radial offset and ensuring that the redundant wear part 52 of the moving ring is always precisely aligned and sealed with the redundant wear part 42 of the stationary ring. This, together with the spring 7, achieves efficient axial wear compensation.

[0055] Examples 3-5 utilize progressive structural optimization to form a mutually compatible and synergistic system. The steel sleeve pressing ring 331 axially presses against the stationary ring 4, while the stationary ring pin 41 radially fixes the stationary ring and the steel sleeve. The "T"-shaped structure of the rotating ring seat radially abuts against the bushing. Multiple positioning ensures no displacement of the stationary and rotating rings, resulting in precise contact of the sealing end faces. Redundant wear portions are designed for both the stationary and rotating rings, and with the axial compensation of the spring 7, the sealing end faces can maintain a continuous seal through "redundant wear + spring push" after wear, significantly extending the component replacement cycle.

[0056] Example 6. This example, based on Example 5, further illustrates the placement position of the first sealing ring, as shown below. Figure 1 As shown, the first sealing ring 91 is disposed between the bushing 1, the lower left side of the rotating ring seat 6, and the rotating ring 5.

[0057] Example 7. This example, based on Example 1, further illustrates the placement of the third sealing ring, as shown below. Figure 1As shown, a third sealing ring 93 is provided at one end of the bushing 1 to prevent the medium from overflowing. The third sealing ring 93 prevents the medium being pumped in the pump (such as slurry or liquid in the food processing field) from overflowing outward from the gap between the bushing 1 and the pump shaft.

[0058] Example 8. This example is based on any one of Examples 1-7 and shows a low-speed rotor pump sealing assembly. The indirect cooling sealing assembly is assembled on the rotor pump and is screwed onto the pump body of the rotor pump through the pump body mounting hole 8. The bushing 1 is assembled onto the pump shaft of the rotor pump.

[0059] In this embodiment, the pump body assembly hole 8 on the component pressing component 2 is used to fix the component and the pump body by passing through the hole and screwing the pump assembly parts into the corresponding screw holes of the rotor pump body; at the same time, the component's bushing 1 is tightly fitted on the outside of the rotor pump shaft to ensure that the bushing 1 rotates synchronously with the pump shaft.

[0060] Rotary pumps are commonly used in the food processing industry to transport viscous slurries (such as fruit and vegetable juices and sauces). The third seal ring 93 of the component can effectively prevent viscous media from overflowing from the gap between the bushing 1 and the pump shaft. The indirect cooling structure does not require complicated pipelines, which is suitable for the low speed and low heat generation characteristics of rotary pumps, and takes into account both sealing reliability and economic use.

[0061] Example 9. This example is based on any one of Examples 1-7 and shows a low-speed cam pump sealing assembly. The indirect cooling sealing assembly is assembled on the cam pump and is screwed onto the pump body of the cam pump through the pump body mounting hole 8. The bushing 1 is assembled onto the pump shaft of the cam pump.

[0062] In this embodiment, the assembly is fixed to the cam pump body by screws through the pump body mounting hole 8, and the bushing 1 is sleeved and fixed to the cam pump shaft to ensure that the bushing 1 rotates synchronously with the pump shaft, and the sealing end faces of the moving ring 5 and the stationary ring 4 are stably fitted.

[0063] The cam pump features stable delivery pressure. The spring 7 of the component can compensate for slight wear on the sealing end face caused by pressure fluctuations through axial compensation, thus extending the seal life. At the same time, the indirect cooling structure avoids contact between the coolant and the delivery medium, making it suitable for the clean delivery needs of cam pumps in food, chemical and other fields.

[0064] Example 10. This example is based on any one of Examples 1-7 and shows a low-speed centrifugal pump sealing assembly. The indirect cooling sealing assembly is assembled on the centrifugal pump and is screwed onto the pump body of the centrifugal pump through the pump body mounting hole 8. The bushing 1 is assembled onto the pump shaft of the centrifugal pump.

[0065] Centrifugal pumps have a wide range of applications (such as water and pharmaceutical liquid transportation). The first and second sealing rings of the components can provide double leak prevention, and the circulating heat dissipation of the cooling chamber 34 can prevent slight heat accumulation on the sealing end face due to long-term operation. The overall structure is simple, reducing the maintenance cost and assembly difficulty of centrifugal pumps, and meeting the cost-effectiveness requirements of low-speed centrifugal pumps.

[0066] The above-disclosed embodiments are merely preferred embodiments of the present utility model and should not be construed as limiting the scope of the present utility model. Therefore, any equivalent variations made in accordance with the scope of the present utility model application shall still fall within the scope of the present utility model.

Claims

1. An indirectly cooled seal assembly comprising a bushing (1), characterized in that, The bushing (1) is provided with the following components from left to right: pressing assembly (2), pressure cap (3), stationary ring (4), moving ring (5), moving ring seat (6), and spring (7); The pressure cap (3) has an inlet hole (31) at one end and an outlet hole (32) at the other end; The pressure cap (3) also includes a steel sleeve (33), which is provided with a cooling cavity (34) connecting the liquid inlet (31) and the liquid outlet (32); The steel sleeve (33) and the stationary ring (4) are fixed by a number of stationary ring pins (41); The bushing (1) has several axial movable grooves (11), the movable ring (5) is connected to the movable ring seat (6), and the movable ring seat (6) is movably connected to the movable grooves (11) through several movable ring pins (51). The number of movable ring pins (51) matches the number of movable grooves (11), and the stationary ring (4) is sealed to the end face of the movable ring (5). The bushing (1) also has a one-way limiting spring groove (12), and the spring groove (12) is provided with the spring (7) for axial compensation of the wear of the end faces of the stationary ring (4) and the moving ring (5); A first sealing ring (91) is provided between the bushing (1), the rotating ring seat (6) and the rotating ring (5), and a second sealing ring (92) is provided between the steel sleeve (33) and the stationary ring (4); The pressing component (2) has a pump body assembly hole (8).

2. The indirectly cooled seal assembly of claim 1, wherein, The pressing assembly (2) includes a locking ring (21) and a pre-fixing block (22) disposed on the locking ring (21) and pressing the steel sleeve (33); Both the locking ring (21) and the pre-fixing block (22) have several screw holes that cooperate with each other. The pre-fixing block (22) is pre-fixed to the locking ring (21) by screws to press the steel sleeve (33). The screw hole of the locking ring (21) corresponds to the pump body assembly hole (8).

3. The indirectly cooled seal assembly of claim 1, wherein, The steel sleeve (33) has a pressing ring (331) extending to one side, which presses the stationary ring (4). The second sealing ring (92) is located between the pressing ring (331) and the stationary ring (4) of the steel sleeve (33).

4. The indirectly cooled seal assembly of claim 3, wherein, The stationary ring (4) has a "convex" cross-section. Its upper side abuts against the pressing ring (331). Its left side is fixed to the steel sleeve (33) by the stationary ring pin (41). Its right side forms a right-angle protrusion to the right, which is the stationary ring redundant wear part (42) and seals the end face of the moving ring (5).

5. The indirectly cooled seal assembly of claim 4, wherein, The moving ring seat (6) has a "T" shaped cross section. A right-angled gap (61) is formed on its left side and connected to the moving ring (5). A portion of the moving ring (5) protrudes from the moving ring seat (6) to seal the end face of the moving ring redundant wear part (52) and the stationary ring redundant wear part (42). Its lower side abuts against the bushing (1), and its right side is movably connected to the movable groove (11) through the moving ring pin (51). Its right end face abuts against the spring (7).

6. The indirectly cooled seal assembly of claim 5, wherein, The first sealing ring (91) is located between the bushing (1), the lower left side of the moving ring seat (6), and the moving ring (5).

7. The indirectly-cooled seal assembly of claim 1, wherein One end of the bushing (1) is provided with a third sealing ring (93) to prevent the medium from overflowing.

8. A low speed rotor pump seal assembly characterized by, The indirect cooling seal assembly according to any one of claims 1-7 is assembled to a rotor pump, and is screwed to the pump body of the rotor pump through the pump body assembly hole (8), and the shaft sleeve (1) is assembled to the pump shaft of the rotor pump.

9. A low speed lobe pump seal assembly characterized by, The indirect cooling seal assembly according to any one of claims 1-7 is assembled to a rotor pump, and is screwed to the pump body of the rotor pump through the pump body assembly hole (8), and the shaft sleeve (1) is assembled to the pump shaft of the rotor pump.

10. A low speed centrifugal pump seal assembly characterized by, The indirect cooling seal assembly according to any one of claims 1-7 is assembled to a rotor pump, and is screwed to the pump body of the rotor pump through the pump body assembly hole (8), and the shaft sleeve (1) is assembled to the pump shaft of the rotor pump.

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