Double-end-face high-pressure-resistant mechanical seal
By deepening the dynamic ring groove, thickening the gasket and improving its position in the inner mechanical seal of the double-end mechanical seal, the problem of leakage caused by O-ring deformation under high pressure is solved, and stronger pressure resistance and a wider range of application are achieved.
Patent Information
- Application Number
- CN202411857704.0
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2024-12-17
- Publication Date
- 2025-02-28
AI Technical Summary
The existing double-end mechanical seal cannot be effectively sealed in high-pressure pumps, causing the O-ring to squeeze into the gap between the push ring and the sleeve under high pressure, affecting the floating ability of the moving ring and possibly causing leakage.
The design of the inner mechanical seal is improved, by deepening the back groove of the moving ring, thickening the gasket and placing the gasket on the inside of the O-ring, preventing the O-ring from deforming under high pressure and squeezed into the gap, while increasing the depth of the inner groove of the moving ring to prevent the gasket from falling out.
It effectively prevents the O-ring from deforming and causing leakage under high pressure, improves the pressure resistance and scope of application of mechanical seals, and ensures that the medium in the equipment does not leak out under the action of high-pressure isolation liquid.
Smart Images
Figure CN119532437A_ABST
Abstract
Description
Technical Field
[0001] The invention relates to the technical field of mechanical seals, and in particular to a double-end-face high-pressure resistant mechanical seal used in an outer sealing cavity under pressurized conditions to prevent leakage of media in equipment under harsh working conditions. Background Art
[0002] Mechanical seal is a new type of shaft seal device with good sealing effect and long service life. The shaft end seals of pump equipment used in the oil refining and chemical industry all adopt mechanical seals. When the mechanical seal is in operation, there will be a very small amount of medium leakage between the friction pairs. The working conditions of the petroleum and petrochemical industry are complex, and there are many flammable, explosive, toxic and harmful, high-temperature and easily gasified media. For these complex working conditions, single-end mechanical seals can no longer meet the requirements, and double-end mechanical seals must be used to ensure that when one set of mechanical seals is damaged, the other set of spare mechanical seals can continue to be used. For some media with a higher risk factor, an isolation fluid with a pressure higher than the medium pressure in the pump needs to be added between the double-end mechanical seals to ensure that the trace leakage between the friction pairs when the pump is operating normally is only the high-pressure isolation fluid leaking into the pump instead of the low-pressure medium leaking out.
[0003] Commonly used ordinary double-end mechanical seals are composed of two sets of ordinary single-end mechanical seals. The working condition of the ordinary single-end mechanical seal design is that the pressure inside the sealing chamber is higher than the pressure outside the sealing chamber (that is, the atmospheric pressure outside the sealing gland), while the working condition of the inner mechanical seal in the pressurized double-end mechanical seal is that the pressure inside the sealing chamber is lower than the pressure outside the sealing chamber. The medium pressure of the medium and low pressure equipment itself is not high, and even if the isolation fluid is pressurized, it will not have much impact on the mechanical seal. However, the pressure inside the high-pressure pump itself is relatively high, and the pressure after pressurization has exceeded the design pressure of the ordinary mechanical seal. Therefore, the inner mechanical seal of the pressurized double-end mechanical seal for the high-pressure pump often has the O-ring of the dynamic ring moving toward the spring seat after being pressurized. Under the action of high pressure, the O-ring squeezes into the gap between the push ring and the sleeve, thereby affecting the floating of the dynamic ring, and even the O-ring and the dynamic ring are separated, causing leakage, so that this structure can only be used for medium and low pressure equipment, and high-pressure pumps cannot be used. Summary of the invention
[0004] The purpose of the present invention is to provide a double-end face high-pressure resistant mechanical seal in view of the deficiencies in the above-mentioned technology. The double-end face mechanical seal can ensure normal operation when the outer sealing chamber is pressurized and the pressure exceeds the maximum pressure that the original single-end face mechanical seal can withstand, thereby ensuring that the medium in the equipment does not leak out under the action of the high-pressure isolation liquid in the outer sealing chamber.
[0005] In view of this, a double-end-face high-pressure resistant mechanical seal of the present invention comprises a shaft sleeve, an inner gland, an outer gland, an inner mechanical seal and an outer mechanical seal; wherein the shaft sleeve is fixedly sleeved on the outer circle of the main shaft of the equipment, the inner gland and the outer gland are installed on the outer side of the equipment cavity from the inside to the outside, the inner gland and the equipment cavity form an inner sealing cavity, the inner mechanical seal is installed in the inner sealing cavity, the outer gland and the inner gland form an outer sealing cavity, the outer mechanical seal is installed in the outer sealing cavity, and the inner mechanical seal and the outer mechanical seal are both sleeved on the outer circle of the shaft sleeve; the outer mechanical seal is an ordinary single-end-face mechanical seal, and the inner mechanical seal is a high-pressure resistant single-end-face mechanical seal;
[0006] The inner mechanical seal comprises a stationary ring and a dynamic ring assembly, wherein the outer sleeve sealing ring of the stationary ring is installed in the groove of the inner pressure cover; the dynamic ring assembly comprises a spring seat, a plurality of springs, a push ring, a gasket, an O-ring, a dynamic ring and a plurality of transmission screws; the spring seat is fixed on the outer circle of the shaft sleeve, the spring seat is provided with a plurality of stepped spring holes and a plurality of stepped through holes opposite to the spring holes, the spring is installed in the spring hole of the spring seat and abuts against the inner side of the push ring, the transmission screw passes through the stepped through hole of the spring seat and is riveted to the inner through hole of the push ring and drives the push ring to rotate together with the spring seat; the outer side of the push ring is provided with a plurality of arc-shaped protrusions protruding inwardly, the inner side of the outer circle of the dynamic ring is provided with a plurality of arc-shaped grooves, the arc-shaped protrusion of the push ring matches the arc-shaped groove of the dynamic ring; the inner groove of the dynamic ring is provided with a gasket and an O-ring, and the gasket is arranged on the inner side of the O-ring.
[0007] Preferably, the outer mechanical seal comprises a stationary ring and a dynamic ring assembly, the outer sleeve sealing ring of the stationary ring is installed in the groove of the outer pressure cover; the dynamic ring assembly comprises a spring seat, a plurality of springs, a push ring, a gasket, an O-ring, a dynamic ring and a plurality of transmission screws; the spring seat is fixed to the outer circle of the shaft sleeve, the spring seat is provided with a plurality of stepped spring holes and a plurality of stepped through holes opposite to the spring holes, the spring is installed in the spring hole of the spring seat and abuts against the inner side of the push ring, the transmission screw passes through the stepped through hole of the spring seat and is riveted to the inner through hole of the push ring; the outer side of the push ring is provided with a plurality of arc-shaped protrusions protruding inwardly, the inner side of the outer circle of the dynamic ring is provided with a plurality of arc-shaped grooves, the arc-shaped protrusions of the push ring match the arc-shaped grooves of the dynamic ring; the inner groove of the dynamic ring is provided with a gasket and an O-ring, and the gasket is arranged on the outer side of the O-ring.
[0008] Preferably, the depth of the inner groove of the moving ring 1 is greater than the depth of the inner groove of the moving ring 2.
[0009] Preferably, the thickness of the gasket 1 is greater than the compressible distance of the spring; the depth of the inner groove of the dynamic ring 1 is greater than the sum of the thickness of the gasket 1 and the cross-sectional length of the O-ring 1 in the working state.
[0010] The beneficial effects of the present invention are:
[0011] 1. The double-end high-pressure mechanical seal of the present invention is an improvement on the structure of the existing mechanical seal by deepening the groove on the back of the dynamic ring, thickening the gasket, and exchanging the positions of the gasket and the O-ring. The installation dimensions are not changed, the applicability is strong, the improvement method is simple and easy to operate.
[0012] 2. The double-end high-pressure resistant mechanical seal of the present invention interchanges the positions of the gasket and the O-ring in the original ordinary mechanical seal. The gasket is located on the inner side of the O-ring, which prevents the O-ring in the inner mechanical seal from being locally deformed and squeezed into the gap between the push ring and the sleeve under the action of the high-pressure isolation fluid in the outer sealing chamber. The thickness of the gasket is greater than the compressible distance of the spring, which can ensure that even if the O-ring is pushed by the outer high-pressure isolation fluid to move the gasket and the push ring toward the inner sealing chamber, causing the spring to be completely compressed into the spring hole, the gasket will not fall out of the groove of the dynamic ring and will be padded on the inner side of the dynamic ring and cannot be reset, thereby solving the problem that the inner mechanical seal of the original pressurized double-end mechanical seal for high-pressure pumps often moves toward the spring seat after the O-ring of the dynamic ring is pressurized, and the O-ring is squeezed into the gap between the push ring and the sleeve under the action of high pressure, thereby affecting the floating performance of the dynamic ring, and even the O-ring is separated from the dynamic ring, causing leakage.
[0013] 3. The double-end-face high-pressure resistant mechanical seal of the present invention adopts a combination of an inner mechanical seal and an outer mechanical seal, so that the pressure resistance of the device is stronger and it is used in high-pressure pumps with a wider range of applications.
[0014] 4. The double-end surface high-pressure resistant mechanical seal of the present invention has a simple structure and a low price, and does not increase the user's operating cost.
[0015] 5. The double-end high-pressure mechanical seal of the present invention can ensure normal operation when the outer sealing chamber is pressurized and the pressure exceeds the maximum pressure that the original single-end mechanical seal can withstand, thereby ensuring that the medium in the equipment does not leak out under the action of the high-pressure isolation liquid in the outer sealing chamber. BRIEF DESCRIPTION OF THE DRAWINGS
[0016] Figure 1 It is a cross-sectional front view of the overall structure of the double-end surface high-pressure resistant mechanical seal of the present invention;
[0017] Figure 2 It is a cross-sectional front view of the inner mechanical seal structure of the present invention;
[0018] Figure 3 This is a structural inner side view of the spring seat 1 of the present invention;
[0019] Figure 4 For the present invention Figure 3 Middle AA section;
[0020] Figure 5 This is an outer side view of a push ring structure of the present invention;
[0021] Figure 6 For the present invention Figure 5 Middle BB section;
[0022] Figure 7 This is an inner side view of the moving ring structure of the present invention;
[0023] Figure 8 For the present invention Figure 7 Middle CC section;
[0024] In the figure: 1. sleeve; 2. inner pressure cover; 3. outer pressure cover; 4. inner sealing chamber; 5. outer sealing chamber; 6. inner mechanical seal; 61. spring seat; 62. spring; 63. push ring; 631. arc-shaped protrusion; 64. gasket; 65. O-ring; 66. moving ring; 661. arc-shaped groove; 662. inner groove of moving ring; 67. stationary ring; 68. transmission screw; 7. outer mechanical seal. DETAILED DESCRIPTION
[0025] The technical solution of the present invention is further described in detail below in conjunction with the accompanying drawings and specific embodiments.
[0026] See also Figure 1 and Figure 2 The present invention provides a double-end high-pressure resistant mechanical seal, comprising a sleeve 1, an inner gland 2, an outer gland 3, an inner mechanical seal 6 and an outer mechanical seal 7; wherein the sleeve 1 is fixedly sleeved on the outer circle of the equipment main shaft, the inner gland 2 and the outer gland 3 are installed from the inside to the outside on the outside of the equipment cavity, the inner gland 2 and the equipment cavity form an inner sealing cavity 4, the inner mechanical seal 6 is installed in the inner sealing cavity 4, the outer gland 3 and the inner gland 2 form an outer sealing cavity 5, the outer mechanical seal 7 is installed in the outer sealing cavity 5, and the inner mechanical seal 6 and the outer mechanical seal 7 are both sleeved on the outer circle of the sleeve 1; the outer mechanical seal 7 is an ordinary single-end mechanical seal, and the inner mechanical seal 6 is a high-pressure resistant single-end mechanical seal.
[0027] In this embodiment, the device housing and the device main shaft form a device cavity. Along the axial direction of the device main shaft, the side close to the device cavity is defined as "inside" or "inner side", and the side away from the device cavity is defined as "outside" or "outer side". The shaft sleeve 1 drives the dynamic ring component 1 in the inner mechanical seal 6 and the dynamic ring component 2 in the outer mechanical seal 7 to rotate together.
[0028] See also Figures 2 to 8As shown, the inner mechanical seal 6 includes a stationary ring 67 and a dynamic ring assembly 1, the outer seal ring of the stationary ring 67 is installed in the groove of the inner pressure cover 2; the dynamic ring assembly 1 includes a spring seat 61, a plurality of springs 62, a push ring 63, a gasket 64, an O-ring 65, a dynamic ring 66 and a plurality of transmission screws 68; the spring seat 61 is fixed to the outer circle of the shaft sleeve 1, and the spring seat 61 is provided with a plurality of stepped spring holes and a plurality of stepped through holes opposite to the spring holes, and the spring 62 is installed in the spring hole of the spring seat 61 and abuts against the inner side of the push ring 63 The driving screw 68 passes through the stepped through hole of the spring seat 61 and is riveted to the inner through hole of the push ring 63, driving the push ring 63 and the spring seat 61 to rotate together; a plurality of arc-shaped protrusions 631 protruding inward are provided on the outer side of the push ring 63, and a plurality of arc-shaped grooves 661 are provided on the inner side of the outer circle of the movable ring 66. The arc-shaped protrusions 631 of the push ring 63 match the arc-shaped grooves 661 of the movable ring; a gasket 64 and an O-ring 65 are installed in the inner groove 662 of the movable ring, and the gasket 64 is arranged on the inner side of the O-ring 65.
[0029] In this embodiment, the stationary ring 67 is installed on the outside of the moving ring assembly 1; the spring seat 61 is fixed to the outer circle of the shaft sleeve 1 by screws, and the shaft sleeve 1 drives the spring seat 61 to rotate. The spring seat 61 drives the push ring 63 to rotate through the transmission screw 68 riveted on the push ring 63; the push ring 63 drives the moving ring 66 to rotate through the arc-shaped protrusion 631 that matches the arc-shaped groove 661 of the moving ring 66. The inner groove 662 of the moving ring refers to the hole opened on the other side parallel to the friction surface of the moving ring 66, that is, the end face of the moving ring 66 close to the equipment cavity, which is used to install the gasket 64 and the O-ring 65.
[0030] The outer mechanical seal 7 includes a stationary ring and a dynamic ring assembly. The outer sealing ring of the stationary ring is installed in the groove of the outer pressure cover 3; the dynamic ring assembly includes a spring seat, a plurality of springs 62, a push ring, a gasket, an O-ring, a dynamic ring and a plurality of transmission screws 68; the spring seat is fixed to the outer circle of the shaft sleeve 1, and the spring seat is provided with a plurality of stepped spring holes and a plurality of stepped through holes opposite to the spring holes. The spring 62 is installed in the spring hole of the spring seat and abuts against the inner side of the push ring. The transmission screw 68 passes through the stepped through hole of the spring seat and is riveted to the inner through hole of the push ring; the outer side of the push ring is provided with a plurality of arc-shaped protrusions protruding inwardly, and the inner side of the outer circle of the dynamic ring is provided with a plurality of arc-shaped grooves, and the arc-shaped protrusions of the push ring match the arc-shaped grooves of the dynamic ring; the inner groove of the dynamic ring is provided with a gasket and an O-ring, and the gasket is arranged on the outer side of the O-ring.
[0031] In this embodiment, the second stationary ring is installed on the outside of the second moving ring assembly; the second spring seat is fixed to the outer circle of the sleeve 1 by screws, and the sleeve 1 drives the second spring seat to rotate. The second spring seat drives the second push ring to rotate through the transmission screw 68 riveted on the second push ring; the second push ring drives the second moving ring to rotate through the arc-shaped protrusion 2 that matches the arc-shaped groove 2 of the second moving ring. The inner groove of the second moving ring refers to the hole opened on the other side parallel to the friction surface of the second moving ring, that is, the end face of the second moving ring close to the equipment cavity, which is used to install the second gasket and the second O-ring.
[0032] The depth of the inner groove 662 of the first moving ring is greater than the depth of the inner groove of the second moving ring.
[0033] In this embodiment, the inner groove 662 of the moving ring 1 is a three-stage stepped through hole. The thickness b of the washer 1 64 is greater than the compressible distance d of the spring 62, that is, b>d; and the inner hole of the washer 1 64 and the outer circle of the shaft sleeve 1 maintain a small clearance fit. The depth a of the inner groove 662 of the moving ring 1 is greater than the sum of the thickness b of the washer 1 and the cross-sectional length c of the O-ring 1 65 in the working state, that is, a>b+c, thereby ensuring that the O-ring 1 65 has a certain degree of freedom in the inner groove 662 of the moving ring 1, ensuring that the moving ring 1 66 will not be swollen to death by the O-ring 1 65.
[0034] The working principle of the above-mentioned double-end high-pressure mechanical seal is as follows: because the O-ring is made of rubber and is compressible, it will deform under pressure to seal small gaps. In order to prevent the O-ring from deforming too much under high pressure and causing damage, a gasket is often set on its low-pressure side to block it and improve its stress state. The pressure in the pump chamber of a general pump mechanical seal is higher than the pressure on the atmospheric side. Therefore, the gasket in an ordinary single-end mechanical seal is set between the O-ring and the moving ring. Toxic and harmful media, especially those with strong harmful media, in order to completely prevent the media in the equipment cavity from leaking out, double-end mechanical seals are used in this working condition, in which an isolation liquid is passed through the outer sealing chamber, and the isolation liquid pressure is greater than the pressure of the media in the inner sealing chamber, to ensure that the isolation liquid can only flow into the equipment, and the toxic and harmful media in the equipment will not leak out. Therefore, the force on the O-ring 1 65 of the inner mechanical seal 6 is opposite to that on the O-ring 2 of the outer mechanical seal 7. If the gasket 2 is arranged between the O-ring 2 and the dynamic ring 2 like the outer mechanical seal 7, the gasket 1 64 will lose its original function of cushioning the low-pressure side of the O-ring 1 65 to protect it. This situation is more obvious in the high-pressure pump. In addition, for the riveting of the driving screw 68, the push ring 1 63 is also processed with a rivet hole for riveting the driving screw 68. After the driving screw 68 is riveted to the push ring 1 63, a hole is left on its end face. If the O-ring 1 65 is directly and tightly fitted with the push ring 1 63 under pressure, the O-ring 1 65 is easily squeezed into these holes and damaged. To this end, the present invention improves the inner mechanical seal 6, and sets a gasket 64 between the push ring 63 and the O-ring 65. The gap between the inner hole of the gasket 64 and the sleeve 1 is small, and the gap between the outer circle of the gasket 64 and the inner groove 662 of the movable ring is small, which can prevent the soft O-ring 65 from being excessively deformed and squeezed into the gap between the push ring 63 and the sleeve 1 under the push of the back high pressure, causing the O-ring 65 to be damaged, and the push ring 63 is squeezed and cannot move along the sleeve 1. At the same time, the thickened gasket 64 is blocked between the O-ring 65 and the push ring 63, and the O-ring 65 does not directly contact the surface of the push ring 63, so as to prevent the O-ring 65 from being damaged by the holes on the surface of the push ring 63 and allow the gasket 64 to improve the stress state of the O-ring 65.
[0035] The working process of the above-mentioned double-end high-pressure mechanical seal is as follows:
[0036] The isolation liquid in the outer sealing chamber 5 is pressurized, and its pressure is higher than the pressure in the equipment sealing chamber, i.e., the inner sealing chamber 4. Since the pressure in the outer sealing chamber 5 is higher than the pressure on the outer side of the outer gland 3 (i.e., the atmospheric pressure), the O-ring 2 in the inner groove of the dynamic ring 2 in the outer mechanical seal 7 is pushed toward the atmospheric end by the pressure in the outer sealing chamber, and the gasket 2 placed on the outer side of the O-ring 2 prevents it from being squeezed into the gap between the inner groove of the dynamic ring 2 and the outer circle of the sleeve 1. The high-pressure isolation liquid in the outer sealing chamber 5 enters the inner portion of the static ring 1 67 in the inner mechanical seal 6. The gap between the hole and the outer circle of the sleeve 1, on the one hand, prevents the toxic and harmful media in the sealing cavity of the equipment from leaking to the outer sealing cavity 5 through the friction pair of the dynamic and static rings of the inner mechanical seal 6 (it can only leak to the inside of the equipment and cannot leak to the outer sealing cavity 5); on the other hand, it will push the O-ring 65 and the gasket 64 to move inside the equipment, in order to prevent the O-ring 65 from being pushed out of the inner groove 662 of the dynamic ring and being padded between the dynamic ring 66 and the push ring 63, so that the dynamic ring 66 cannot float with the rotation of the main shaft of the equipment. Compared with the outer mechanical seal 7, in the inner mechanical seal 6, the installation positions of the gasket and the O-ring are changed, that is, the gasket 64 is moved from the outer side of the O-ring 65 to the inner side of the O-ring 65. Because the original gasket is thin, if the medium pressure fluctuates greatly, the spring 62 of the inner mechanical seal 6 is completely compressed into the spring hole of the spring seat 61, which will cause the gasket 64 to fall out of the inner groove 662 of the dynamic ring. Therefore, the gasket 64 is thickened and the depth of the inner groove 662 of the dynamic ring is increased to ensure that no matter how the medium pressure fluctuates, the gasket 64 and the O-ring 65 can be in the normal working position without falling out. Once the medium pressure returns to normal, the gasket 64 and the O-ring 65 can quickly return to their original positions to ensure the normal operation of the equipment.
Claims
1. A double-end high-pressure mechanical seal, characterized in that: It comprises a shaft sleeve, an inner gland, an outer gland, an inner mechanical seal and an outer mechanical seal; wherein the shaft sleeve is fixedly sleeved on the outer circle of the main shaft of the equipment, the inner gland and the outer gland are installed from the inside to the outside on the outside of the equipment cavity, the inner gland and the equipment cavity form an inner sealing cavity, the inner mechanical seal is installed in the inner sealing cavity, the outer gland and the inner gland form an outer sealing cavity, the outer mechanical seal is installed in the outer sealing cavity, and the inner mechanical seal and the outer mechanical seal are both sleeved on the outer circle of the shaft sleeve; the outer mechanical seal is an ordinary single-end mechanical seal, and the inner mechanical seal is a high-pressure resistant single-end mechanical seal; The inner mechanical seal comprises a stationary ring and a dynamic ring assembly, wherein the outer sleeve sealing ring of the stationary ring is installed in the groove of the inner pressure cover; the dynamic ring assembly comprises a spring seat, a plurality of springs, a push ring, a gasket, an O-ring, a dynamic ring and a plurality of transmission screws; the spring seat is fixed on the outer circle of the shaft sleeve, the spring seat is provided with a plurality of stepped spring holes and a plurality of stepped through holes opposite to the spring holes, the spring is installed in the spring hole of the spring seat and abuts against the inner side of the push ring, the transmission screw passes through the stepped through hole of the spring seat and is riveted to the inner through hole of the push ring and drives the push ring to rotate together with the spring seat; the outer side of the push ring is provided with a plurality of arc-shaped protrusions protruding inwardly, the inner side of the outer circle of the dynamic ring is provided with a plurality of arc-shaped grooves, the arc-shaped protrusion of the push ring matches the arc-shaped groove of the dynamic ring; the inner groove of the dynamic ring is provided with a gasket and an O-ring, and the gasket is arranged on the inner side of the O-ring.
2. The double-end surface high pressure resistant mechanical seal according to claim 1, characterized in that: The outer mechanical seal comprises a stationary ring 2 and a dynamic ring assembly 2, wherein the outer sleeve sealing ring of the stationary ring 2 is installed in the groove of the outer pressure cover; the dynamic ring assembly 2 comprises a spring seat 2, a plurality of springs, a push ring 2, a gasket 2, an O-ring 2, a dynamic ring 2 and a plurality of transmission screws; the spring seat 2 is fixed to the outer circle of the shaft sleeve, the spring seat 2 is provided with a plurality of stepped spring holes and a plurality of stepped through holes opposite to the spring holes, the spring is installed in the spring hole of the spring seat 2 and abuts against the inner side of the push ring 2, the transmission screw passes through the stepped through hole of the spring seat 2 and is riveted to the inner through hole of the push ring 2; the outer side of the push ring 2 is provided with a plurality of arc-shaped protrusions 2 protruding inwardly, the inner side of the outer circle of the dynamic ring 2 is provided with a plurality of arc-shaped grooves 2, the arc-shaped protrusions 2 of the push ring 2 match the arc-shaped grooves 2 of the dynamic ring 2; the inner groove of the dynamic ring 2 is provided with a gasket 2 and an O-ring 2, and the gasket 2 is arranged on the outer side of the O-ring 2.
3. The double-end surface high pressure resistant mechanical seal according to claim 2, characterized in that: The depth of the inner groove of the moving ring 1 is greater than the depth of the inner groove of the moving ring 2.
4. The double-end surface high pressure resistant mechanical seal according to claim 1, characterized in that: The thickness of the washer 1 is greater than the compressible distance of the spring; the depth of the inner groove of the dynamic ring 1 is greater than the sum of the thickness of the washer 1 and the cross-sectional length of the O-ring 1 in the working state.