CN210318503U

CN210318503U - Mechanical sealing device

Info

Publication number: CN210318503U
Application number: CN201921113455.9U
Authority: CN
Inventors: 毛方; 郝木明; 郭崇斌; 任宝杰; 王曰升; 丁康杰; 贾丹; 王志鹏
Original assignee: DONGYING HISCIEN SEALING TECHNOLOGY CO LTD
Current assignee: DONGYING HISCIEN SEALING TECHNOLOGY CO LTD
Priority date: 2019-07-16
Filing date: 2019-07-16
Publication date: 2020-04-14
Anticipated expiration: 2029-07-16

Abstract

The utility model provides a mechanical seal device includes first sealed, first sealed first rotating ring and the first quiet ring that has the phase-match setting, first rotating ring suit is on the axle sleeve, first quiet ring sets up on first gland offer the first inlet that is used for flushing fluid to flow in on the first gland set up at least one fluid chamber that is used for the cooling on the first quiet ring, fluid chamber and first inlet intercommunication. The fluid cavity communicated with the first fluid inlet is formed in the first stationary ring, so that the flushing fluid directly flows into the first stationary ring, the heat can be quickly dissipated, and huge heat generated by friction of a high-temperature medium and the sealing end face is effectively prevented from being transferred into the first stationary ring; the sealing ring at the matching part of the first static ring and the first gland can be effectively prevented from losing efficacy due to the expansion deformation of the first static ring, so that the sealing medium is prevented from leaking; the flow speed of the high-temperature medium near the sealing end face can be increased.

Description

Mechanical sealing device

Technical Field

The utility model belongs to the technical field of mechanical seal, concretely relates to mechanical seal device.

Background

With the increasing development of industries such as petroleum, chemical engineering, aerospace, natural gas transportation and the like, the requirements on mechanical sealing are higher and higher, and zero leakage and zero escape of a sealing process medium are required to be realized for mechanical sealing under some special working conditions (such as high temperature, high rotating speed and larger shaft diameter). The mechanical seal must meet the requirements of long service life, simple installation and operation, low maintenance cost and the like. For common contact type mechanical seal, in the operation and operation process, the seal end faces of the moving ring and the static ring are mutually rubbed and abraded, so that a large amount of friction heat is generated, the temperature between the seal end faces is rapidly increased, huge thermal stress is generated, the seal end faces are seriously subjected to phase change, such as vaporization, cavitation erosion and the like, so that the abrasion is aggravated, the service life of the seal is seriously shortened, the moving ring and the static ring are in a dry friction state in the operation process, the seal end faces are subjected to thermal deformation at high temperature, the phenomena of thermal cracking, blister and the like of the seal end faces are caused, in addition, the seal end faces are excessively high in temperature, and the seal ring can be hardened and deformed. The problems are very easy to cause the failure of the mechanical seal, the service life and the service efficiency of the mechanical seal are greatly reduced, and the use cost of a user is increased.

Disclosure of Invention

An object of the utility model is to overcome the problem that above-mentioned exists, provide a mechanical sealing device, effectively reduce the inside and seal face temperature of sealing ring, reduce hot crack, the blister that the seal face produced and scar phenomenons such as, improve sealed mechanical properties, prolong sealed life, improve availability factor.

The utility model discloses a realize that the technical scheme that above-mentioned purpose was taken is:

in order to achieve the technical purpose, the utility model adopts the following technical scheme:

the utility model provides a mechanical seal device includes first sealed, first sealed first rotating ring and the first quiet ring that has the phase-match setting, first rotating ring suit is on the axle sleeve, first quiet ring sets up on first gland offer the first inlet that is used for washing the fluid inflow on the first gland offer at least one fluid chamber that is used for the cooling on the first quiet ring, fluid chamber and first inlet intercommunication.

Furthermore, a plurality of fluid cavities which are coaxially arranged at intervals are arranged in the circumferential direction of the first stationary ring, and the fluid cavities are sector-ring-shaped.

Further, the fluid cavity is arranged opposite to the sealing end face of the first movable ring in the radial direction.

Furthermore, the distance between the fluid cavity and the sealing end face of the first stationary ring is 1.2-1.8 mm.

Further, the ratio of the radial dimension of the fluid cavity to the radial dimension of the first stationary ring is 0.3 to 0.5.

Further, the distance between two adjacent fluid cavities is 3-6 mm.

Furthermore, the fluid cavity is provided with a guide hole extending outwards in the radial direction, an annular fluid inlet groove is formed in the first gland, and the fluid inlet groove is communicated with the guide hole.

Further, the radial guide hole is located at the axial center of the stationary ring.

Furthermore, one side that the fluid cavity is being close to the axle head is the opening end set up annular play liquid groove on the first gland and with the first liquid outlet of play liquid groove intercommunication, the opening end and play liquid groove intercommunication.

Furthermore, a first flow dividing hole and a second flow dividing hole which are communicated with the first liquid inlet are formed in the first pressing cover, and flushing fluid flowing out of the second flow dividing hole is used for flushing the first sealed sealing end face.

Furthermore, the outer side of the sealing end face of the first seal is a high-pressure medium cavity, and the inner side of the sealing end face of the first seal is a low-pressure fluid cavity.

Furthermore, a micro groove is formed in the sealing end face of the first movable ring, and the micro groove comprises a circumferential groove extending in the circumferential direction and a reverse groove inclining outwards along one end of the circumferential groove.

Further, the inclination direction of the reverse groove is opposite to the rotation direction of the first rotating ring.

Furthermore, the molded line of the reverse groove is a logarithmic spiral line, and the helical angle is 15-30 degrees.

Furthermore, the groove depth of the reverse groove is 5-15 mu m.

Furthermore, the groove depth of the circumferential groove is 5-15 mu m.

Further, the groove depth of the reverse groove is greater than or equal to the groove depth of the circumferential groove.

Further, the ratio of the radial dimension to the circumferential dimension of the micro grooves is 0.6 to 2.0.

Further, the ratio of the radial dimension of the reverse groove to the radial dimension of the circumferential groove is 0.5-1.5.

Further, the circumferential groove land ratio of the micro groove is 0.8 to 1.5.

Furthermore, the ratio of the radial dimension of the micro groove to the radial dimension of the sealing end face of the first movable ring is 0.3-0.7.

Further, mechanical seal device includes that the pump is imitated the ring and is close to the second of axle head sealed, and the second is sealed including the second rotating ring of suit on the axle sleeve and the second stationary ring of setting on the second gland, the pump is imitated the ring and is divided into the first low-pressure chamber that is close to the axle head with the low pressure fluid cavity and keep away from the second low-pressure chamber of axle head. Further, the pumping ring pumps the liquid from the first low pressure chamber to the second low pressure chamber.

Furthermore, a second liquid inlet for flushing fluid to flow in, a liquid inlet hole communicated with the first low-pressure cavity and used for flushing the sealed end face of the second seal, and a liquid outlet hole communicated with the second low-pressure cavity are formed in the second gland.

The mechanical sealing device provided by the utility model has the advantages that the fluid cavity communicated with the first inlet is arranged on the first stationary ring, so that the flushing fluid directly flows into the first stationary ring, the heat can be rapidly dissipated, and the huge heat generated by the friction of the high-temperature medium and the sealing end surface is effectively prevented from being transferred into the first stationary ring; the sealing ring at the matching part of the first static ring and the first gland can be effectively prevented from losing efficacy due to the expansion deformation of the first static ring, so that the sealing medium is prevented from leaking; the flowing speed of the high-temperature medium near the sealing end face can be increased, and phase change of the high-temperature medium fluid around the sealing end face, such as vaporization and cavitation, can be further prevented; and the thermal deformation, the heat crack and the like of the first seal can be reduced, the stability of the seal structure is improved, and the service life of the seal is prolonged. The fluid cavity is arranged, so that the weight of the first stationary ring can be reduced, the dynamic balance performance of the first seal is improved, and the energy consumption is reduced.

Other features and advantages of the present invention will become more apparent from the following detailed description of the invention when read in conjunction with the accompanying drawings.

Drawings

Fig. 1 is a schematic structural diagram of an embodiment of a mechanical sealing device according to the present invention;

FIG. 2 is an enlarged view of the first seal of FIG. 1;

FIG. 3 is an enlarged view of the second seal of FIG. 1;

FIG. 4 is a schematic structural view of an end surface of the first stationary ring near the shaft end;

fig. 5 is a schematic structural view of a sealing end face of the first rotating ring.

Detailed Description

In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the drawings in the embodiments of the present invention are combined below to clearly and completely describe the technical solutions in the embodiments of the present invention.

In the description of the present invention, it should be noted that the direction close to the axis in the radial direction in the normal use state is "inside", and the direction far from the axis is "outside". The terminology is for the purpose of describing the invention only and is not intended to be limiting of the invention since it is not intended to indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation. Moreover, the terms "first," "second," and "third" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance; the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "a plurality" means two or more unless specifically limited otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," and "fixed" are to be construed broadly and may, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meaning of the above terms in the present invention can be understood according to specific situations by those skilled in the art.

Referring to fig. 1-5, an embodiment of the mechanical sealing device according to the present invention includes a shaft sleeve 20 fixed on a rotating shaft 10, a first gland 40 engaged with a pump cavity 30, and a second gland 50 engaged with the first gland 40, wherein the second gland 50 is close to one side of a shaft end, i.e. close to an air side; in order to achieve sealing of the shaft ends, a first seal 60 is provided at a distance from the shaft ends and a second seal 70 is provided at a position close to the shaft ends, the first seal 60 being close to the medium side, the left side in fig. 1; the second seal 70 is near the air side, right in fig. 1.

Referring to fig. 2, the first seal 60 has a first movable ring 61, a first stationary ring 62, a first push ring 63, a first spring and a first spring seat 65, which are arranged in a matching manner, the first movable ring 61 is sleeved on the shaft sleeve 10, and the first stationary ring 62 is fixed on the first gland 40; specifically, the first spring seat 65 is fixed on the shaft sleeve 10, the first movable ring 61 is axially movably arranged on the first spring seat 65, a plurality of first springs are circumferentially arranged on the first spring seat 65 at intervals, one end of each first spring is arranged in the first spring seat 65, one end of each first spring is attached to the first push ring 63, and the first push ring 63 transmits the elastic force of each first spring to the first movable ring 61 for realizing the axial movement of the first movable ring 61. When the rotating shaft 10 rotates, the shaft sleeve 10 rotates along with the rotating shaft, so that the first movable ring 61, the first push ring 63, the first spring and the first spring seat 65 are driven to rotate, sealing is realized between the first movable ring 61 and the first stationary ring 62, and high-temperature media are prevented from leaking towards the shaft end through the sealing end face; the seal end surfaces of the first seal 60 include a seal end surface 611 of the first moving ring 61 and a seal end surface 621 of the first stationary ring 62.

Referring to fig. 1, the outer side of the sealing end surface of the first rotating ring 61 is a high-pressure medium chamber 101, the inner side is a low-pressure fluid chamber 102, the high-pressure medium chamber 101 is a high-temperature high-pressure working medium, the low-pressure fluid chamber 102 is a low-pressure fluid, and the fluid pressure in the high-pressure medium chamber 101 is greater than the fluid pressure in the low-pressure fluid chamber 102.

When the rotating shaft 10 operates, the high-temperature medium fluid pressure in the high-pressure medium cavity 101 and the elastic force formed by the first spring between the first spring seat 65 and the first push ring 63 jointly act on the first moving ring 61, so that the moving ring moves towards the direction in which the first stationary ring 62 approaches, the sealing end surface tends to close, and a sealing effect is realized, and besides, the sealing ring at the matching position of the first moving ring 61 and the shaft sleeve 10 also plays a very key auxiliary sealing effect.

Referring to fig. 1 and 2, when the rotating shaft 10 rotates at a high speed, a large part of the large pressure generated by the high-temperature medium fluid may be collected at the sealing end surface 611 of the first rotating ring 61, thereby accelerating friction and wear of the sealing end surface, causing deformation of the sealing end surface, stress concentration, and the like. In order to reduce the temperature of the sealing end face of the first seal 60, a first liquid inlet 41 for the inflow of the flushing fluid is formed in the first gland 40, at least one fluid cavity 622 for reducing the temperature is formed in the first stationary ring 62, the fluid cavity 622 is communicated with the first liquid inlet 41, and the flushing fluid is introduced into the fluid cavity 622 through the first liquid inlet 41 to reduce the temperature of the sealing end face of the first seal 60.

The fluid cavity 622 communicated with the first fluid inlet 41 is formed in the first stationary ring 62, so that the flushing fluid directly flows into the first stationary ring 62, heat can be quickly dissipated, and huge heat generated by friction of a high-temperature medium and a sealing end face is effectively prevented from being transferred into the first stationary ring 62; the sealing ring failure at the matching part of the first static ring 62 and the first gland 40 caused by the expansion deformation of the first static ring 62 can be effectively prevented, and the sealing medium leakage is further caused; the flow speed of the high-temperature medium near the sealing end face of the first seal 60 can be increased, and phase change of the high-temperature medium fluid around the sealing end face, such as vaporization and cavitation, can be further prevented; and the thermal deformation, the heat crack and the like of the first seal 60 can be reduced, the stability of the sealing structure is improved, and the service life of the seal is prolonged. The fluid cavity 622 also reduces the weight of the first stationary ring 62, improves the dynamic balance performance of the first seal 60, and reduces energy consumption.

First stationary ring 62 and first gland 40 keep relative still at the operation in-process, the sealed terminal surface of first seal 60 is the ring shape, in order to reach better cooling effect, be equipped with the fluid cavity 622 that a plurality of coaxial intervals set up in the circumference of first stationary ring 62, let in the flushing fluid respectively in to a plurality of fluid cavities 622, timely take away the heat on the first stationary ring 62, make the temperature of first stationary ring 62 reduce, heat on the sealed terminal surface 611 of rotatory first rotating ring 61 continues to transmit first stationary ring 62, make the temperature of first rotating ring 61 also reduce.

In this embodiment, the size of the sealing end surface 611 of the first rotating ring 61 in the radial direction is much smaller than the size of the sealing end surface 621 of the first stationary ring 62 in the radial direction, and frictional heat generated during rotation is mainly located in the sealing end surface 611 of the first rotating ring 61 and the corresponding portion of the sealing end surface 621 of the first stationary ring 62; in order to achieve better heat dissipation effect, the fluid cavity 622 is arranged opposite to the sealing end surface 611 of the first rotating ring 61, that is, the outer diameter and the inner diameter of the fluid cavity 622 are arranged to be the same as those of the sealing end surface 611 of the first rotating ring 61, or the outer diameter and the inner diameter of the fluid cavity 622 are arranged to be coincident with those of the sealing end surface 611 of the first rotating ring 61, that is, the fluid cavity 622 is identical to or partially coincident with the sealing end surface 611 in the radial dimension, so that the fluid cavity 622 is arranged at a position closer to the sealing end surface 611 of the first rotating ring 61, which is beneficial to transferring heat into the fluid cavity 622 as soon as possible, being carried away by flushing fluid, and achieving temperature reduction. The fluid cavity 622 is preferably formed in a sector ring shape coaxially disposed with the first stationary ring 62, which is advantageous for the sealing end surface 611 of the first movable ring 61 to correspond to, and improve the heat dissipation efficiency. Preferably, the distance between the fluid cavity 622 and the sealing end face 621 of the first stationary ring 62 is set to be 1.2-1.8 mm, so that heat between the fluid cavity 622 and the sealing end face 621 of the first stationary ring 62 can be rapidly transferred, heat energy dissipation at the sealing end face 621 of the first stationary ring 62 and the sealing end face 611 of the first movable ring 61 is facilitated, and the temperature of the sealing end face of the first seal 60 is reduced to the maximum extent. The ratio of the axial dimension of the fluid cavity 622 to the axial dimension of the first stationary ring 62 is 0.8 to 0.95.

The radial size and the axial size of the fluid cavity 622 are critical, the radial size and the axial size are too small to achieve a good cooling effect, and the radial size and the axial size are too large to reduce the rigidity and the strength of the first stationary ring 62, so that deformation is caused; preferably, the ratio of the radial dimension of the fluid cavity 622 to the radial dimension of the first stationary ring 62 is set to 0.3-0.5, and the distance between two adjacent fluid cavities 622 is set to 3-6 mm.

The flushing fluid flowing into the first liquid inlet 41 is divided into two paths, wherein one path of the flushing fluid flows into the fluid cavity 622 for cooling the first stationary ring 62, the other path of the flushing fluid is used for flushing the sealing end face of the first seal 60, the sealing end face 621 of the first stationary ring 62 and the sealing end face 611 of the first movable ring 61 are cooled, accumulated impurities are flushed away, temperature rise between the sealing end faces is reduced, and the service life of the seal is prolonged. Specifically, a first flow dividing hole 42 and a second flow dividing hole 43 which are communicated with a first liquid inlet 41 are arranged on the first gland 40, and the first flow dividing hole 42 is communicated with the fluid cavity 622; the flushing fluid exiting the second flow-dividing opening 43 is used to flush the sealing face of the first seal 60, and the outlet of the second flow-dividing opening 43 is located outside the sealing face of the first seal 60.

In order to rapidly inject the flushing fluid into the fluid cavity 622, the first stationary ring 62 is provided with flow guide holes 623 extending outward along the radial direction of the fluid cavity 622, and the flow guide holes 623 correspond to the fluid cavity 622 one by one; an annular liquid inlet groove 44 is formed in the first gland 40, the first flow dividing hole 42 is communicated with the liquid inlet groove 44, and the liquid inlet groove 44 is communicated with the flow guide hole 623. One side of the fluid cavity 622 close to the shaft end is an open end, the first gland 40 is provided with an annular liquid outlet groove 45 and a first liquid outlet 46 communicated with the liquid outlet groove 45, and the open end is communicated with the liquid outlet groove 45; the open end is provided to facilitate manufacturing of the fluid cavity 622 and to facilitate outflow of the flushing fluid within the fluid cavity 622, ensuring a fluid flow rate. The flushing fluid flowing into the first flow dividing hole 42 through the first inlet 41 then flows into the annular fluid inlet groove 44, and then flows into the fluid chambers 622 after passing through the flow guide holes 623 respectively; the flushing fluid in the fluid cavities 622 then enters the annular exit slot 45 and then passes through the first exit port 46 to carry away heat; a circulating flow of flushing fluid can be achieved.

In order to prevent the flushing fluid flowing through the first flow dividing hole 42 from leaking, a groove is respectively formed on the left side and the right side of the flow guiding hole 623, and the first sealing ring 81 is arranged in the groove to ensure that the flushing fluid flows into the flow guiding hole 623 and is prevented from flowing into the high-pressure medium cavity 101 for conveying the high-temperature medium. Set up second sealing washer 82 in the internal diameter side of first gland 40 and first stationary ring 62 for prevent that flushing fluid from flowing into low pressure fluid chamber 102, just so can guarantee that flushing fluid flows in circulation through first liquid outlet 46 along first inlet 41 on first gland 40 at last, and the cooling channel who forms flows, and then takes away the heat that produces in the sealed terminal surface department of first seal 60 through the form of heat exchange, plays the cooling effect to sealed terminal surface and first stationary ring 62, improves sealed use mission.

The flow path of the flushing fluid in the first stationary ring 62 is that the flushing fluid flows radially inwards along the flow guide hole 623 at first and then reaches the fluid cavity 622, and moves axially in the fluid cavity 622, and the diameter of the flow guide hole 623 is set to be the same as the radial dimension of the fluid cavity 622, so that uniform flow of the flushing fluid is guaranteed, uniform flushing of the first stationary ring by the flushing fluid is guaranteed, a self-cooling effect is achieved, and huge heat generated by friction of an external high-temperature fluid medium and a sealing end face can be effectively prevented from being transferred to the inside of the first stationary ring 62.

Referring to fig. 5, in order to further increase the sealing between the sealing end surface 621 of the first stationary ring 62 and the sealing end surface 611 of the first rotating ring 61, a plurality of micro grooves 612 are formed in the sealing end surface 611 of the first rotating ring 61, and the micro grooves 612 are uniformly arranged at intervals in the circumferential direction of the sealing end surface 611. The micro-groove 612 includes a circumferential groove 6121 extending in the circumferential direction and a reverse groove 6122 inclined outward along one end of the circumferential groove 6121, wherein the inclination direction of the reverse groove 6122 is opposite to the rotation direction of the first rotating ring 61. The micro-groove 612 is arranged to form a pumping effect when the rotating shaft 10 rotates, which is beneficial to forming uniform liquid film seal between the sealing end surface 621 of the first stationary ring 62 and the sealing end surface 611 of the first movable ring 61; the micro-grooves 612 including the circumferential grooves 6121 and the reverse grooves 6122 are beneficial to averaging the fluid pressure between the sealing end faces, effectively avoiding cavitation of fluid in the groove area, enhancing the self-lubrication of the sealing end faces, realizing the first seal 60 in a full liquid film lubrication state, improving the high temperature and high pressure resistance of the sealing device, reducing the friction and abrasion of the sealing end faces, reducing the excessive friction heat generated in the friction process and prolonging the service life of the seal.

The molded line of the circumferential groove 6121 is an arc line, the molded line of the reverse groove 6122 is a logarithmic spiral, and the spiral angle of the logarithmic spiral is 15-30 degrees; the groove depth of the circumferential groove 6121 is 5-15 μm, the groove depth of the reverse groove 6122 is 5-15 μm, and the sealed air film has high rigidity under the parameters, so that the optimal sealing performance can be obtained. The groove depth of the reverse groove 6122 and the circumferential groove 6121 may be the same or different, and the groove depth of the reverse groove 6122 is not less than the groove depth of the circumferential groove 6121. The ratio of the radial dimension of the inverted groove 6122 to the radial dimension of the circumferential groove 6121 is 0.5 to 1.5. The micro groove 612 is shaped like an inclined L, and the radial boundary line of the micro groove 612 is a logarithmic spiral and the axial boundary line is an arc line, preferably an arc line arranged coaxially with the first stationary ring 61.

The ratio of the radial dimension to the circumferential dimension of the micro groove 612 is 0.6-2.0, the ratio of the circumferential groove land of the micro groove 612 is 0.8-1.5, and the ratio of the radial dimension of the micro groove 612 to the radial dimension of the sealing end surface 611 of the first rotating ring 61 is 0.3-0.7. Specifically, when the inner radius of the sealing end surface 611 of the first moving ring 61 is defined as ri, the outer radius is defined as ro, the inner radius of the circumferential groove 6121 is defined as rg1, the outer radius is defined as rg2, and the outer radius of the inverted groove 6122 is defined as rg3, the ratio of the radial dimension of the inverted groove 6122 to the radial dimension of the circumferential groove 6121 (rg3-rg 2)/(rg 2-rg1) = 0.5-1.5, the ratio of the radial dimension of the micro groove 612 to the radial dimension of the sealing end surface 611 of the first moving ring 61 (rg3-rg1)/(ro-ri) = 0.3-0.7, the circumferential groove land ratio bb/cc = 0.8-1.5 of the micro groove 612, the groove region in the circumferential direction is a groove region, and the region which is not opened is a land region.

The second seal 70 comprises a second movable ring 71 sleeved on the shaft sleeve 10 and a second stationary ring 72 arranged on the second gland 50, the pumping ring 90 is adjacent to the second gland 50 in the axial direction, and the pumping ring 90 divides the low-pressure fluid chamber 102 into a first low-pressure chamber 1021 near the shaft end and a second low-pressure chamber 1022 far away from the shaft end; as the rotary shaft 10 rotates, the pumping ring 90 pumps the fluid in the first low pressure chamber 1021 to the second low pressure chamber 1022. A second liquid inlet 51 for flushing fluid to flow in, a liquid inlet hole 52 communicated with the first low-pressure cavity 1021, and a liquid outlet hole 53 communicated with the second low-pressure cavity 1022 are formed in the second gland 50, and the liquid inlet hole 52 is communicated with the second liquid inlet 51 and used for flushing the sealing end face of the second seal 70; thereby realize that the flush fluid circulates to play liquid hole 53 by buffering second inlet 51 fast, makes the clean effect of flush fluid better, the more rapid heat of taking away to realize safe sealed effect.

While the invention has been described with reference to a preferred embodiment, it will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention. However, any simple modification, equivalent change and modification made to the above embodiments according to the technical substance of the present invention still belong to the protection scope of the technical solution of the present invention.

Claims

1. The utility model provides a mechanical seal device, includes first sealed, first sealed first rotating ring and the first quiet ring that has the phase-match setting, first rotating ring suit is on the axle sleeve, first quiet ring sets up on first gland, its characterized in that set up on the first gland and be used for washing the first inlet that the fluid flowed in set up at least one fluid chamber that is used for the cooling on the first quiet ring, fluid chamber and first inlet intercommunication.

2. The mechanical seal of claim 1, wherein a plurality of coaxially spaced fluid chambers are disposed circumferentially around the first stationary ring, the fluid chambers being of a fan-ring shape.

3. The mechanical seal of claim 1, wherein a ratio of a radial dimension of the fluid chamber to a radial dimension of the first stationary ring is 0.3 to 0.5.

4. The mechanical sealing device according to claim 1, wherein the fluid chamber has a guide hole extending radially outward, and an annular fluid inlet groove is formed in the first gland and is communicated with the guide hole.

5. The mechanical seal device according to claim 1, wherein the fluid chamber is an open end on a side close to the shaft end, an annular liquid outlet groove and a first liquid outlet communicated with the liquid outlet groove are formed on the first gland, and the open end is communicated with the liquid outlet groove.

6. A mechanical seal according to any of claims 1 to 5 wherein a micro groove is provided in the sealing end face of the first rotating ring, said micro groove comprising a circumferentially extending circumferential groove and an opposing groove inclined outwardly along one end of said circumferential groove.

7. A mechanical seal according to claim 6 wherein the direction of inclination of said counter sink is opposite to the direction of rotation of said first rotating ring.

8. The mechanical seal of claim 6, wherein the ratio of the radial dimension to the circumferential dimension of the micro grooves is 0.6 to 2.0.

9. A mechanical seal according to claim 6 wherein the ratio of the radial dimension of the counter sink to the radial dimension of the circumferential sink is 0.5 to 1.5.

10. A mechanical seal according to claim 6 wherein the ratio of the radial dimension of the micro-groove to the radial dimension of the seal face of the first rotating ring is from 0.3 to 0.7.