Mechanical sealing structure and compressor

Abstract

The utility model discloses a mechanical seal structure and a compressor, which comprise a static ring, a moving ring and a transition ring rotating in the same direction as the moving ring, the transition ring is arranged between the moving ring and the static ring at intervals, and the rotating speed of the transition ring relative to the moving ring is controlled by a speed regulator. And the rotating speed of the transition ring is smaller than that of the moving ring. The transition ring is arranged between the moving ring and the static ring, the moving ring and the static ring are spaced and cannot make direct contact, the transition ring rotates through the speed regulator, but the rotating speed of the transition ring is made to be smaller than that of the moving ring, so that the rotating speed of the moving ring and the rotating speed of the static ring can be adjusted. Therefore, the linear speed of the movable ring relative to the transition ring is smaller than the rotating speed of the input shaft, and under the condition that the rotating speed of the movable ring relative to the static ring is not changed, the end face relative speed of the movable ring and the end face relative speed of the static ring are both lower than the limited linear speed allowed by the end faces.

Description

Technical Field

[0001] The utility model relates to the technical field of shaft sealing, in particular to a mechanical sealing structure and a compressor. Background Art

[0002] A mechanical seal is a device that is perpendicular to the end face of a rotating shaft and keeps the end face in close contact and slides relative to the end face under the cooperation of elastic force or other forces to prevent fluid leakage. Mechanical seals are usually composed of static rings, dynamic rings, elastic elements and other components. When the dynamic ring is running at high speed, the end face of the dynamic ring or the static ring will produce certain wear due to relative friction. This wear is greatly affected by the relative linear velocity between the end faces. The greater the relative linear velocity of the two end faces, the faster the wear. In order to reduce wear, mechanical seals strictly stipulate the linear velocity. For example, the friction linear velocity of some mechanical seals cannot exceed the limit value of 30m / s. However, when the diameter of the rotating shaft is large, the diameters of the static ring and the dynamic ring are also large, which makes the linear velocity of the relative rotation of the static ring and the dynamic ring too large, exceeding the limit value of the allowable linear velocity. For example, when the rotation speed of a shaft with a diameter of 120mm reaches 4775 rpm and 3000 rpm, the friction linear velocity of the mechanical seal exceeds the limit value of 30m / s. Therefore, how to reduce the relative velocity of the end faces of the dynamic and static rings without affecting the input rotation speed has become a technical problem that needs to be solved urgently in the industry. Utility Model Content

[0003] In order to solve the problem of large relative linear speed of dynamic and static rings of mechanical seal, the utility model proposes a mechanical seal structure and a compressor, by arranging a transition ring between the dynamic ring and the static ring, so that the relative linear speed of the end faces of the dynamic and static rings is lower than the limited speed.

[0004] The technical solution adopted by the utility model is that the mechanical sealing structure includes a static ring, a dynamic ring, and also includes a transition ring that rotates in the same direction as the dynamic ring. The transition ring is arranged between the dynamic ring and the static ring at intervals. The rotation speed of the transition ring relative to the dynamic ring is controlled by a speed regulator, so that the rotation speed of the transition ring is less than the rotation speed of the dynamic ring.

[0005] In some embodiments, the speed regulator includes a damper, which acts as a damping speed limiter on the rotation of the transition ring.

[0006] In certain embodiments, the damper is a magnetic or hydraulic rotary damper.

[0007] In some embodiments, the speed regulator includes a transmission, an input end of the transmission is driven by the dynamic ring, and an output end of the transmission is connected to drive the transition ring.

[0008] In certain embodiments, the transmission includes a first face gear coaxially fixed relative to the moving ring and a second face gear coaxially fixed relative to the stationary ring, the first face gear and the second face gear are arranged opposite to each other, and the first face gear and the second face gear are simultaneously engaged with a transmission gear, the gear shaft of the transmission gear is perpendicular to the moving ring shaft, and the gear shaft is connected to the transition ring.

[0009] In certain embodiments, an axial groove is provided on the transition ring, and the end of the gear shaft is slidably fitted in the axial groove.

[0010] In certain embodiments, a drive ring is coaxially sleeved outside the transition ring, the transmission gear is located between the transmission gear and the drive ring, and the gear shaft is connected to the drive ring.

[0011] In some embodiments, the first face gear, the second face gear and the transmission gear are all bevel gears, the transmission gear is slidably sleeved on the gear shaft, and a support spring is sleeved on the gear shaft between the transmission gear and the drive ring.

[0012] In certain embodiments, the hardness of the stationary ring material is greater than that of the transition ring, and the hardness of the transition ring is greater than that of the dynamic ring.

[0013] In some embodiments, the material of the end surface of the transition ring facing the dynamic ring is the same as that of the end surface of the stationary ring, and the material of the end surface of the transition ring facing the stationary ring is the same as that of the end surface of the dynamic ring.

[0014] A compressor comprises the mechanical sealing structure.

[0015] Compared with the prior art, the utility model has the following beneficial effects:

[0016] The utility model provides the transition ring between the moving ring and the stationary ring to separate the moving ring from the stationary ring so that they cannot directly contact each other. The transition ring is rotated by a speed regulator. However, as long as the rotation speed of the transition ring is made smaller than the rotation speed of the moving ring, the linear speed of the moving ring relative to the transition ring is smaller than the rotation speed of the input shaft, that is, smaller than the rotation speed of the moving ring relative to the stationary ring. Since the rotation speed of the transition ring is smaller than the rotation speed of the moving ring, the rotation speed of the transition ring relative to the stationary ring is also smaller than the rotation speed of the moving ring relative to the stationary ring. That is, without changing the rotation speed of the moving ring relative to the stationary ring, the relative speeds of the end faces of the moving ring and the stationary ring are both lower than the limited linear speed allowed by the end faces. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] The present invention is described in detail below in conjunction with specific embodiments and drawings. In order to show details and facilitate understanding of its principles, it is not necessarily drawn to scale, and similar reference numerals may describe similar components in different views. The drawings generally illustrate the embodiments discussed herein by way of example and not limitation. Among them:

[0018] Figure 1 It is a schematic diagram of the mechanical seal structure arrangement and the compressor housing.

[0019] Figure 2 yes Figure 1 A magnified schematic diagram of center A.

[0020] Figure 3 yes Figure 2 A magnified schematic diagram of point B in the middle.

[0021] Figure 4 The second embodiment Figure 2 A magnified schematic diagram of point B in the middle.

[0022] Figure 5 It is a schematic diagram of the transition ring of the second embodiment moving toward the stationary ring after being worn.

[0023] Figure 6 It is a schematic diagram of the cooperation between the transition ring and the transmission gear in the second embodiment.

[0024] Figure 7 This is a schematic diagram of the cooperation between the second face gear and the stationary ring.

[0025] Figure 8 It is a schematic diagram of embodiment 3.

[0026] In the figure, 1. static ring; 2. dynamic ring; 3. transition ring; 4. input shaft; 5. annular cavity; 6. rotating ring plate; 7. first face gear; 8. second face gear; 9. transmission gear; 10. gear shaft; 11. axial slide groove; 12. drive ring; 13. support spring; 14. outer rotor motor; 15. pressure-resistant casing; 16. ring preload spring. DETAILED DESCRIPTION

[0027] The following are specific embodiments of the present invention, and the technical solution of the present invention is further described in conjunction with the accompanying drawings, but the present invention is not limited to these embodiments, and the following embodiments do not limit the utility model involved in the claims. In addition, all combinations of the features described in the embodiments are not necessarily required for the solution of the utility model.

[0028] The principle and structure of the present utility model are described in detail below with reference to the accompanying drawings and embodiments. Example

[0029] A mechanical seal is a device that is perpendicular to the end face of a rotating shaft and keeps the end face in close contact and slides relative to the end face under the cooperation of elastic force or other forces to prevent fluid leakage. Mechanical seals are usually composed of static rings, dynamic rings, elastic elements and other components. When the dynamic ring is running at high speed, the end face of the dynamic ring or the static ring will produce certain wear due to relative friction. This wear is greatly affected by the relative linear velocity between the end faces. The greater the relative linear velocity of the two end faces, the faster the wear. In order to reduce wear, mechanical seals strictly stipulate the linear velocity. For example, the friction linear velocity of some mechanical seals cannot exceed the limit value of 30m / s. However, when the diameter of the rotating shaft is large, the diameters of the static ring and the dynamic ring are also large, which makes the linear velocity of the relative rotation of the static ring and the dynamic ring too large, exceeding the limit value of the allowable linear velocity. For example, when the rotation speed of a shaft with a diameter of 120mm reaches 4775 rpm and 3000 rpm, the friction linear velocity of the mechanical seal exceeds the limit value of 30m / s. Therefore, how to reduce the relative velocity of the end faces of the dynamic and static rings without affecting the input rotation speed has become a technical problem that needs to be solved urgently in the industry.

[0030] For this reason, Figure 1 , 2 As shown in Figure 3, a mechanical seal structure is provided, comprising a stationary ring 1, a dynamic ring 2, and a transition ring that rotates in the same direction as the dynamic ring 2, wherein the transition ring is arranged between the dynamic ring 2 and the stationary ring 1 at intervals, and the speed of the transition ring relative to the dynamic ring 2 is controlled by a speed regulator, so that the speed of the transition ring is less than the speed of the dynamic ring 2. For example, the speed regulator can be an active control device such as a motor, so as to independently adjust the speed of the transition ring, so that the speed of the transition ring is less than that of the dynamic ring 2. The dynamic ring 2 is usually sleeved on the input shaft 3 of the equipment and rotates with the input shaft 3, while the stationary ring 1 is slidably sleeved on the input shaft 3 and cannot rotate with the input shaft 3.

[0031] The beneficial effect of such arrangement is that: since the rotational speed of the moving ring 2 is the same as the speed of the input shaft 3, the speed of the moving ring 2 relative to the stationary ring 1 is the speed of the input shaft 3. When the rotational speed exceeds the limited linear speed allowed by the moving ring 2 relative to the stationary ring 1, if the moving ring 2 is in direct contact with the stationary ring 1 at this time, the linear speed of the moving ring 2 relative to the stationary ring 1 exceeds the limited linear speed allowed by the moving ring 2 relative to the stationary ring 1. For this reason, the transition ring is provided between the moving ring 2 and the stationary ring 1 to separate the moving ring 2 from the stationary ring 1 so that they cannot be in direct contact with each other. The transition ring is rotated by the speed regulator, but as long as the rotational speed of the transition ring is made smaller than the rotational speed of the moving ring 2, the linear speed of the moving ring 2 relative to the moving ring 2 is smaller than the rotational speed of the input shaft 3, that is, smaller than the rotational speed of the moving ring 2 relative to the stationary ring 1. Since the rotational speed of the transition ring is smaller than the rotational speed of the moving ring 2, the rotational speed of the transition ring relative to the stationary ring 1 is also smaller than the rotational speed of the moving ring 2 relative to the stationary ring 1. That is, without changing the rotational speed of the moving ring 2 relative to the stationary ring 1, the relative speeds of the end faces of the moving ring 2 and the stationary ring 1 are both lower than the limited linear speed allowed by the end faces.

[0032] The speed regulator of this embodiment is a damper, which plays a role of damping and limiting the speed of the rotation of the transition ring. For example, the transition ring can be connected to a rotation damper to provide additional resistance to the rotation of the transition ring.

[0033] A rotary damper is a device used to control the motion of a rotating system. It is usually composed of hydraulic, mechanical or electronic components and can provide damping and control in a mechanical system to prevent excessive oscillation or vibration. In engineering and mechanical design, rotary dampers are commonly used for shock absorption, smoothing motion and controlling rotational speed.

[0034] The beneficial effect of such a setting is that the speed of the transition ring is controlled by damping, the control is simple and convenient, and it is suitable for the situation where the running speed of the input shaft 3 occasionally exceeds the limited speed instantaneously. At this time, due to the existence of damping, the speed of the transition ring can be prevented from exceeding the limited speed, so that the rotation speed of the transition ring relative to the static ring 1 is also smaller than the rotation speed of the dynamic ring 2 relative to the static ring 1, so that the relative speed of the end faces of the dynamic ring 2 and the static ring 1 are both lower than the limited linear speed allowed by the end faces.

[0035] Specifically, the damper can be a magnetic or hydraulic rotation damper. The rotation damper of the specific embodiment includes a fixed annular cavity, and two rotating rings are coaxially connected to the transition ring and extend into the annular cavity. Damping fluid is stored in the annular cavity, thereby damping the rotation of the two rotating rings.

[0036] A hydraulic rotary damper is a device that uses the principles of fluid dynamics to achieve rotational damping. The working principle of a hydraulic rotary damper is based on shear force and viscous damping. When the rotating ring 2 rotates, the liquid forms a shear layer between the rotating ring 2 and the annular cavity, which hinders the movement of the rotating ring 2. This shear causes energy to be converted into heat, which slows down the speed of the rotating ring 2. By adjusting the viscosity of the liquid, the geometry of the rotating ring 2 and the annular cavity, and the design of the blades, different degrees of damping effect can be achieved.

[0037] The beneficial effects of such a setting are:

[0038] Magnetic or hydraulic rotary dampers have simple structures and are easy to integrate and set up. Example

[0039] like Figure 4 , 5 As shown in , 6 and 7, the speed regulator includes a transmission, the input end of the transmission is driven by the moving ring 2, and the output end of the transmission is connected to drive the transition ring. Since the moving ring 2 and the transition ring are coaxial rotating parts, according to the principle of mechanical transmission, the two rotating parts can be provided with a transmission to achieve variable speed transmission, thereby making the speeds of the two different, so that the speed of the transition ring is lower than that of the moving ring 2, so that the relative linear speed of each contact end surface is lower than the limited speed.

[0040] The beneficial effects of such a setting are:

[0041] The transmission is used to always maintain a fixed speed difference between the dynamic ring 2 and the transition ring, so that the speed of the transition ring relative to the static ring 1 is always smaller than the speed of the dynamic ring 2, so that the dynamic ring 2 can operate at a speed exceeding the limited speed for a long time.

[0042] Specifically, the present embodiment adopts that the transmission includes a first face gear fixed coaxially relative to the moving ring 2 and a second face gear fixed coaxially relative to the stationary ring 1, the first face gear and the second face gear are arranged opposite to each other, and the first face gear and the second face gear are simultaneously meshed with a transmission gear, the gear shaft of the transmission gear is perpendicular to the axis of the moving ring 2, that is, perpendicular to the input shaft 3, and the gear shaft is connected to the transition ring. The first face gear is fixedly connected to the moving ring 2, so that the first face gear and the moving ring 2 rotate synchronously, and the second face gear is fixed relative to the stationary ring 1, that is, the second face gear is stationary.

[0043] The beneficial effects of such a setting are:

[0044] The first face gear rotates with the moving ring 2, and the first face gear drives the transmission gear to rotate. Since the second face gear is relatively fixed, the transmission gear rotates around its axis and revolves around the input shaft 3 at the same time, which is equivalent to a planetary gear. Since the gear shaft of the transmission gear is connected to the transition ring, the revolution of the transmission gear drives the transition ring to rotate around the input shaft 3. From the principle of gear transmission, it can be seen that the rotation speed of the first face gear is twice that of the transition ring.

[0045] The transition ring is provided with an axial sliding groove, and the end of the gear shaft is slidably fitted in the axial sliding groove.

[0046] The beneficial effects of such a setting are:

[0047] As the transition ring is used, the end face will wear and the wear will make the transition ring thinner. Under the pressure of the axial force of the dynamic ring 2, the transition ring will move toward the static ring 1. Since the transition ring is provided with an axial groove, the gear shaft will not block the axial movement of the transition ring, which is beneficial to the axial movement of the transition ring, thereby ensuring the fit between the end face of the transition ring and the end face of the static ring 1 to ensure the sealing effect.

[0048] A driving ring 2 is coaxially sleeved outside the transition ring, the transmission gear is located between the transmission gear and the driving ring 2 , and the gear shaft is connected to the driving ring 2 .

[0049] The beneficial effects of such a setting are:

[0050] By providing the drive ring 2, all the transmission gears are fixed together, so that the radial position of each transmission gear is fixed. At the same time, since all the transmission gears are integrated together, it is also convenient to fix and install the transmission gears and ensure that the transmission is more stable.

[0051] The first face gear, the second face gear and the transmission gear are all bevel gears. The transmission gear is slidably sleeved on the gear shaft. A supporting spring is sleeved on the gear shaft between the transmission gear and the driving ring 2 .

[0052] The beneficial effects of such a setting are:

[0053] The use of bevel gears is not only conducive to the realization of the face gear transmission system, but also conducive to the radial movement of the transmission gear, so that the transmission gear can adapt to the change of the distance between the first face gear and the second face gear. For example, when the distance between the first face gear and the second face gear increases, the transmission gear can be moved radially toward the center so that the transmission gear can still mesh with the first face gear and the second face gear at the same time. The support spring is set to always apply a preset thrust force toward the center to the transmission gear, thereby ensuring that no matter how the distance between the first face gear and the second face gear changes, the transmission gear is closely meshed with the first face gear and the second face gear, thereby maintaining a stable transmission of the rotation speed.

[0054] In terms of materials, the hardness of the static ring 1 is greater than that of the transition ring, and the hardness of the transition ring is greater than that of the dynamic ring 2.

[0055] The beneficial effects of such a setting are:

[0056] The performance and durability of the seal are ensured by making the relatively rotating parts use materials of different hardness. Generally speaking, the material of the dynamic ring 2 is relatively soft, while the material of the static ring 1 is relatively hard, which can provide better sealing performance and stability during the sealing process. In order to ensure that the relatively rotating parts still meet the contact relationship of materials of different hardness after the transition ring is separated between the dynamic ring 2 and the static ring 1, the hardness of the static ring 1 material is greater than the hardness of the transition ring, and the hardness of the transition ring is greater than the hardness of the dynamic ring 2, so that the hardness relationship of each contact surface still meets the matching relationship of the material hardness from the side with high speed to the side with low speed from soft to hard. The material of the dynamic ring 2 is usually a relatively soft material, such as a rubber material or a soft polymer. The hardness of these materials is generally in a lower range, so that they can better adapt to the changes of the sealing surface during the movement and ensure the good sealing performance of the seal.

[0057] Alternatively, the material of the end face of the transition ring facing the dynamic ring 2 is the same as the material of the end face of the stationary ring 1, and the material of the end face of the transition ring facing the stationary ring 1 is the same as the material of the end face of the dynamic ring 2.

[0058] The beneficial effects of such a setting are:

[0059] By using materials with different hardness on the end faces of the transition ring, the relative relationship of the material hardness of the two end faces that rotate relative to each other is made the same as the relationship of the end face material hardness when the dynamic ring 2 is in direct contact with the static ring 1. As a result, after the transition ring is spaced between the dynamic ring 2 and the static ring 1, the matching relationship of the relative hardness of the end face materials of the dynamic ring 2 and the static ring 1 remains unchanged. Example

[0060] like Figure 8 As shown, unlike the embodiment, the second face gear is not fixed relative to the stationary ring 1, but is controlled to rotate by an external rotor motor, so that the speed of the second face gear can be adjusted as needed, and then the revolution speed of the transmission gear can be controlled together with the first face gear, so that the rotation speed of the transition ring can be adjusted as needed and is not affected by the rotation speed of the dynamic ring 2, so as to make the relative linear speeds of different contact end faces different, so that the end faces rotate at a better relative speed.

[0061] An external rotor motor, in which the rotor (i.e. the rotating part) is located outside the motor, and the stator (i.e. the fixed part) is located inside. The stator part is fixedly sleeved on the stationary ring 1.

[0062] The compressor includes the above-mentioned mechanical seal structure, wherein the dynamic ring 2 in the mechanical seal structure is mounted on the input shaft 3 of the screw compressor, and the static ring 1 in the mechanical seal is mounted on the mechanical seal cover plate or the pressure-resistant housing 4. When the input shaft 3 rotates, the dynamic ring 2 and the static ring 1 of the mechanical seal will form a friction pair to achieve the dynamic sealing function. At the same time, with the friction between the dynamic ring 2 and the static ring 1, the dynamic ring 2 gradually generates friction loss. At this time, the pre-tightening spring of the dynamic ring 2 will push the dynamic ring 2 to move forward, thereby ensuring the effectiveness of the mechanical seal. A transition ring and a speed regulator for controlling the transition ring are arranged between the dynamic ring 2 and the static ring 1.

[0063] The relative speed of the stationary ring 1 and the dynamic ring 2 of the compressor mechanical seal structure is one of the important factors affecting the wear of the mechanical seal. In the mechanical seal, there is a relative movement between the stationary ring 1 and the dynamic ring 2, and their relative speed determines the wear of the seal surface. When the relative speed of the stationary ring 1 and the dynamic ring 2 is low, the friction between the seal surfaces is relatively small. In this case, the wear is mainly affected by friction and the degree of wear is relatively light. However, even at a low relative speed, long-term operation will cause wear and fatigue, especially when the sealing medium has particles or solid impurities. When the relative speed of the stationary ring 1 and the dynamic ring 2 is high, the friction between the seal surfaces increases, resulting in increased wear. High-speed rotation will generate greater inertial and centrifugal forces, which aggravate the wear of the seal. In this case, wear may be faster and the life of the seal may be shorter. Therefore, the design and selection of the seal needs to take into account the relative speed under actual operating conditions. Generally, mechanical seals running at high speeds require additional measures to reduce wear.

[0064] The specific embodiments described herein are merely examples of the spirit of the present invention. Those skilled in the art may make various modifications or additions to the specific embodiments described, or replace them in similar ways, without departing from the spirit of the present invention or exceeding the scope defined by the appended claims.

[0065] Although some terms are used more frequently in this article, the possibility of using other terms is not excluded. These terms are used only to more conveniently describe and explain the essence of the utility model; interpreting them as any additional restrictions is contrary to the spirit of the utility model. The execution order of actions, steps, etc. in the devices and methods shown in the specification and the drawings can be implemented in any order as long as there is no special explicit limitation on the order and the output of the previous processing is not used in the subsequent processing. Similar sequential terms (for example, "first", "next", "secondly", "again", "then", etc.) used for the convenience of description do not mean that they must be implemented in such an order.

[0066] It should be understood by those skilled in the art that all directional references (for example, above, below, upward, up, downward, down, top, bottom, left, right, vertical, horizontal, etc.) are used descriptively in the drawings to facilitate the reader's understanding, and do not represent limitations (for example, on position, orientation or use, etc.) on the scope of the present invention as defined by the appended claims. They are only for the convenience of describing the present application and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the referred device or element must have a specific orientation or be constructed and operated in a specific orientation. The directional words "inside and outside" refer to the inside and outside relative to the outline of each component itself.

[0067] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" may include both "above" and "below". The device may also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0068] In addition, some vague terms (e.g., substantially, certain, generally, etc.) may refer to slight inaccuracies or slight deviations of conditions, quantities, values, or dimensions, some of which are within the manufacturing deviation or tolerance range. It should be noted that the use of words such as "first" and "second" to define components is only for the convenience of distinguishing the corresponding components. If not otherwise stated, the above words have no special meanings and therefore cannot be understood as limiting the scope of protection of this application.

Claims

1. A mechanical seal structure, including a stationary ring and a dynamic ring, characterized in that: It also includes a transition ring that rotates in the same direction as the dynamic ring. The transition ring is arranged between the dynamic ring and the static ring. The rotation speed of the transition ring relative to the dynamic ring is controlled by a speed regulator, so that the rotation speed of the transition ring is less than the rotation speed of the dynamic ring. The speed regulator includes a damper, which plays a role in damping and speed limiting the rotation of the transition ring.

2. The mechanical seal structure according to claim 1, characterized in that: The damper is a magnetic or hydraulic rotary damper.

3. The mechanical seal structure according to claim 1, characterized in that: The speed regulator comprises a transmission, the input end of the transmission is driven by the moving ring, and the output end of the transmission is connected to drive the transition ring.

4. The mechanical sealing structure according to claim 3, characterized in that: The transmission includes a first face gear coaxially fixed relative to the moving ring and a second face gear coaxially fixed relative to the stationary ring. The first face gear and the second face gear are arranged opposite to each other. The first face gear and the second face gear are simultaneously engaged with a transmission gear. The gear shaft of the transmission gear is perpendicular to the moving ring shaft, and the gear shaft is connected to the transition ring.

5. The mechanical seal structure according to claim 4, characterized in that: The transition ring is provided with an axial sliding groove, and the end of the gear shaft is slidably fitted in the axial sliding groove.

6. The mechanical seal structure according to claim 5, characterized in that: A driving ring is coaxially sleeved outside the transition ring, the transmission gear is located between the transmission gear and the driving ring, and the gear shaft is connected to the driving ring.

7. The mechanical seal structure according to claim 6, characterized in that: The first face gear, the second face gear and the transmission gear are all bevel gears. The transmission gear is slidably sleeved on the gear shaft. A supporting spring is sleeved on the gear shaft between the transmission gear and the driving ring.

8. The mechanical seal structure according to claim 1, characterized in that: The hardness of the static ring material is greater than that of the transition ring, and the hardness of the transition ring is greater than that of the dynamic ring.

9. The mechanical seal structure according to claim 1, characterized in that: The material of the end surface of the transition ring facing the dynamic ring is the same as that of the end surface of the stationary ring, and the material of the end surface of the transition ring facing the stationary ring is the same as that of the end surface of the dynamic ring.

10. A compressor, characterized in that Comprising the mechanical sealing structure according to any one of claims 1 to 9.

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