High efficiency circulating cooling device for mechanical seal

Abstract

The invention relates to a high-efficiency circulating cooling device for mechanical seal, comprising a gland, a stationary ring assembly mounted on the gland, a dynamic ring assembly rotating with a rotating shaft and a pumping ring rotating with the dynamic ring assembly. The gland is provided with a flow-guiding heat sink for guiding flushing liquid entering from a flushing liquid inlet to the matching end faces of the stationary ring assembly and the dynamic ring assembly. The heat-conducting heat sink can force the flushing liquid to be introduced into the end faces of the stationary ring assembly and the dynamic ring assembly to forcibly take away the heat. Meanwhile, the heat-conducting heat sink can also conduct heat quickly to ensure that the sealing heat is taken away in time, and a stable and reliable liquid film can be formed on the end face. Meanwhile, the flow groove is optimized and improved on the ordinary flow channel, adopts an eccentric circle, and is divided into several sections to form a flow channel, which has the effect of significantly increasing fluid pressure and reducing flow resistance, and the pumping groove is a double-crescent-shaped structure. The pumping ring of this shape has the best pressure and flow rate among all closed pumping rings, and the flow rate is 2 to 3 times that of other structures under the same size.

Description

Technical Field

[0001] The invention relates to a mechanical sealing device, in particular to a high-efficiency circulating cooling device for mechanical sealing. Background Art

[0002] Mechanical seals will generate friction heat and stirring heat during operation. If this heat is not dissipated in time, it will affect the performance of the mechanical seal. Therefore, corresponding cooling measures need to be taken to cool the mechanical seal. In the mechanical seal flushing system specified in API682: PLAN23, PLAN52, and PLAN53 all require the seal to have a self-contained circulation device to provide circulation power for the flushing liquid. However, due to the size of the equipment cavity, the size used to design the circulation device is very limited. In these flushing schemes, the key to the success or failure of the mechanical seal is whether the circulation volume of the circulation device and the heat of the seal can be taken away in time. Inlet and outlet holes are respectively opened on the gland of the mechanical seal. The medium in the gland cavity is transported to the external heat exchanger through the built-in pumping ring of the mechanical seal cavity, and then returned to the gland cavity after heat exchange. The circulation effect of the circulation mechanism on the coolant in this cooling scheme has a great influence on the cooling effect.

[0003] The patent with the authorization announcement number CN103233920B discloses a circulating cooling mechanism of a mechanical seal device for a pump, including a gland 1, a stationary ring assembly 2, a dynamic ring assembly 4, and a pumping ring 6. A circulating liquid outlet 7 and a circulating liquid inlet 8 are provided on the gland 1. The stationary ring assembly 2 is installed on the gland 1, and the dynamic ring assembly 4 is installed on the shaft or the sleeve to rotate with the shaft. The friction ring of the dynamic ring assembly 4 rotates with the friction ring of the stationary ring assembly 2 to form a mechanical seal. The pumping ring 6 is fixedly connected to the tail seat of the dynamic ring assembly 4 and rotates with the dynamic ring assembly. The outer ring portion of the pumping ring 6 corresponds to the circulating liquid outlet 7 provided on the gland 1 and the gland 1. The inner cavity annular surface cooperates to form a centrifugal pumping mechanism, grooves 60 are distributed on the middle circumference of the pumping ring surface 61 of the pumping ring 6 to form blades 61, and labyrinth sealing grooves 65 are respectively opened on the left and right sides of the pumping ring surface 61 of the pumping ring 6. A circulation groove 16 is opened on the inner ring surface 10 of the gland 1 corresponding to the blade 61 of the pumping ring 6. The circulation groove 16 is not opened at the circulating liquid outlet 7 on the corresponding gland 1, forming a partition convex stopper 15, and a drainage outlet hole 7' connected to the circulating liquid outlet 7 is opened on the bottom surface of the circulation groove 16 on the front side of the convex stopper 15, and an axial liquid inlet groove 17 connected to the circulation groove 16 is opened on the inner ring surface 10 of the gland 1 at the rear side near the circulating liquid inlet 8 (the direction is determined by the turning of the pumping ring 6), so that the circulation groove 16 is connected to the rear side of the circulating liquid inlet 8.

[0004] During use, the coolant enters the inner cavity of the gland 1 from the circulating liquid inlet 8, then performs a circular motion along the inner cavity of the gland 1, and finally flows from the axial liquid inlet groove 17 to the annular flow groove 16, and then comes out from the circulating liquid outlet 7. During this process, due to the circular motion of the coolant, the circulating liquid entering the inner cavity of the gland 1 will be subjected to a large centrifugal force. Under the action of the centrifugal force, most of the coolant entering the inner cavity of the gland 1 flows away from the inner cavity of the gland 1 away from the stationary ring assembly 2 and the dynamic ring assembly 4, thereby reducing the coolant flow near the stationary ring assembly 2 and the dynamic ring assembly 4, causing a large amount of heat to remain in the coolant around the stationary ring assembly 2 and the dynamic ring assembly 4, resulting in unsatisfactory heat dissipation of the stationary ring assembly 2 and the dynamic ring assembly 4, seriously affecting the life, reliability and safety of the seal. Summary of the invention

[0005] The object of the present invention is to provide a high-efficiency circulating cooling device for mechanical seal, which has the advantage of good heat dissipation effect.

[0006] The above technical objectives of the present invention are achieved through the following technical solutions: a high-efficiency circulating cooling device for mechanical seal, comprising a gland, a stationary ring assembly installed on the gland, a dynamic ring assembly rotating with the rotating shaft and a pumping ring rotating with the dynamic ring assembly, the dynamic ring assembly and the stationary ring assembly cooperate to form a mechanical seal, the gland is provided with a flushing liquid inlet and a flushing liquid outlet, an inner cavity is formed between the gland and the dynamic ring assembly and the stationary ring assembly, the flushing liquid inlet is connected to the inner cavity, a pumping cavity is formed between the pumping ring and the gland, a blocking protrusion is provided on the gland, the blocking protrusion is located in the pumping cavity, and the flushing liquid outlet is connected to the inner cavity. The outlet is connected to the pumping chamber, and the pumping ring is provided with a pumping groove facing the pumping chamber side. The inner chamber and the pumping chamber are connected through a flushing liquid inlet. The connecting point between the inner chamber and the pumping chamber is located on one side of the blocking protrusion, and the connection point between the flushing liquid outlet and the pumping chamber is located on the other side of the blocking protrusion. The pressure cover is provided with a guide heat sink for guiding the flushing liquid entering the flushing liquid inlet to the mating end faces of the static ring assembly and the dynamic ring assembly. The guide heat sink is located in the inner chamber and is arranged around the inner chamber. The guide heat sink is located between the flushing liquid inlet and the pumping ring, and a flow gap for the flushing liquid to pass through is formed between the guide heat sink and the friction ring of the dynamic ring assembly.

[0007] Through the above technical scheme, the flushing liquid entering the inner cavity from the flushing liquid inlet will be forced to be guided between the dynamic ring assembly and the static ring assembly under the action of the guide heat sink, so that the heat generated between the dynamic ring assembly and the static ring assembly can be taken away in time, effectively avoiding the situation where the temperature of the dynamic ring assembly and the static ring assembly is too high during use, ensuring that the sealing heat is taken away in time, and a stable and reliable liquid film can be formed at the sealing end face, thereby improving the life, reliability and safety of the seal.

[0008] Preferably, the width of the flow gap is not less than 2.5 mm.

[0009] Through the above technical solution, in order to ensure that the flushing liquid can pass smoothly through the flow gap, the width of the flow gap is set to be no less than 2.5 mm. When the flow gap is less than 2.5 mm, the flow rate of the flushing liquid will decrease sharply, affecting the circulation of the entire flushing liquid, resulting in a large amount of heat retained in the inner cavity, and ultimately affecting the normal operation of the mechanical seal and the service life of the mechanical seal.

[0010] Preferably, the thermal conductivity of the guide heat sink is greater than the thermal conductivity of the pressure cover.

[0011] Through the above technical scheme, in order to dissipate the heat from the dynamic ring assembly and the static ring assembly faster, the guide heat sink is made of a material with a higher thermal conductivity. During operation, the guide heat sink absorbs the heat emitted by the dynamic ring assembly and the static ring assembly, and then transfers it to the pressure cover, and then dissipates it to the outside. Since the thermal conductivity of the guide heat sink is high, the heat transfer ability is stronger, and it is easier to transfer the heat from the dynamic ring assembly and the static ring assembly to the pressure cover.

[0012] Preferably, the cross section of the pumping groove along the direction perpendicular to the axis of the pumping ring is an arc-shaped groove, and the cross section of the pumping groove along the axis passing through the pumping ring is an arc-shaped groove.

[0013] Through the above technical solution, the structure of the pumping groove of this shape is "double arc". Through a large number of experiments, it is verified that this shape of pumping groove is the optimal structure. At the same size, the flow rate is 2 to 3 times that of pumping grooves of other structures. It can greatly improve the pumping effect of the pumping ring and greatly increase the flow rate of the flushing liquid in the inner cavity and the pumping cavity, so that the flushing liquid can take away more heat in the same time.

[0014] Preferably, the ratio of the width of the pumping groove to the distance between two adjacent pumping grooves is 3 / 2 to 5 / 2.

[0015] Through the above technical solution, in order to ensure the pumping capacity of the pumping ring, it is necessary to strictly control the width of the pumping groove and the distance between adjacent pumping grooves. After a large number of tests and verifications, when the ratio of the width of the pumping groove to the distance between two adjacent pumping grooves is 2 / 5~2 / 3, the pumping effect of the pumping ring is best.

[0016] Preferably, the inner cavity is an annular cavity, the angle between the diameter of the inner cavity and the central axis of the flushing liquid inlet is a, the angle between the diameter of the inner cavity and the central axis of the flushing liquid outlet is b, both angle a and angle b are acute angles, the angle c between the velocity direction of the flushing liquid entering the flushing liquid inlet and the velocity direction of the flushing liquid in the pumping chamber is an acute angle, and the angle d between the velocity direction of the flushing liquid in the flushing liquid outlet and the velocity direction of the flushing liquid in the pumping chamber is an acute angle.

[0017] Through the above technical scheme, the flushing liquid entering the inner cavity from the flushing liquid inlet can flow along a tangential direction close to the inner cavity, while the flushing liquid already in the inner cavity makes a circular motion along the inner cavity. Therefore, the flushing liquid entering along a direction close to the tangential direction will push the existing flushing liquid, thereby increasing the speed of the flushing liquid in the inner cavity, accelerating the movement speed of the flushing liquid, and allowing the flushing liquid to take away more heat in the same time. Similarly, the flushing liquid outlet is arranged in this way to facilitate the flushing liquid to quickly exit the pumping cavity.

[0018] Preferably, a flow groove is provided on the pressure cover, the pumping ring is located at the opening of the flow groove, and the pumping groove faces the flow groove, the pumping cavity is formed between the pumping ring and the flow groove, the flushing liquid entering the pumping cavity from the flushing liquid inlet flows out from the flushing liquid outlet along the pumping cavity, and the depth of the flow groove gradually deepens from the flushing liquid inlet to the flushing liquid outlet along the flow direction of the flushing liquid.

[0019] Through the above technical scheme, the gradually deepening shape of the flow groove can reduce the liquid flow resistance. At the same time, the flow groove arranged in this way can play a role in strengthening the power of the flushing liquid, further enhancing the circulation effect, making the flushing liquid flow faster in the pumping chamber, and then making the flushing liquid in the inner cavity flow faster, thereby increasing the heat dissipation capacity.

[0020] Preferably, the blocking protrusion is provided with an arc surface on the side facing the flushing liquid outlet, and the connecting point between the flushing liquid outlet and the pumping chamber is located on the arc surface.

[0021] Through the above technical solution, when the flushing liquid flows to the blocking bump, the flushing liquid will contact the curved surface. At this time, since the flushing liquid speed is relatively fast and the space at the blocking bump gradually becomes smaller, the flushing liquid will accumulate rapidly at the blocking bump along the curved surface. At this time, the pressure of the flushing liquid will increase sharply, and then the flushing liquid will flow out from the flushing liquid outlet. Therefore, the pressure of the flushing liquid flowing out from the flushing liquid outlet is relatively high, which is convenient for cooling the flushing liquid in the later stage, and avoids the situation where the flow rate is too slow due to insufficient flushing liquid pressure when cooling the flushing liquid.

[0022] Preferably, the angle between the flushing liquid inlet and the flushing liquid outlet is 130-160 degrees.

[0023] Through the above technical scheme, it is possible to prevent the flushing liquid entering from the flushing liquid inlet from directly entering the pumping chamber from the flushing liquid inlet. Since the flushing liquid inlet is located between the pumping chamber and the inner chamber, the flushing liquid moving from the inner chamber will first move in a circle in the inner chamber. Only when the inner chamber is filled will the flushing liquid enter the pumping chamber from the flushing liquid inlet. Therefore, it is possible to ensure that the flushing liquid moves along the inner chamber for at least one circle. Therefore, the flushing liquid has a uniform and obvious cooling effect on the entire static ring assembly and the dynamic ring assembly, thereby avoiding the deformation of the friction ring of the dynamic ring assembly and the friction ring of the static ring assembly when the temperature is uneven.

[0024] In summary, the beneficial effects of the present invention compared with the prior art are as follows:

[0025] (1) Through a large number of experimental verifications, this shape of pumping ring has the best pressure and flow rate among all closed pumping rings, and the flow rate is 2 to 3 times that of other structures with the same size;

[0026] (2) The flow channel is optimized and improved on the ordinary flow channel. It uses an eccentric circle and is divided into several sections to form a flow channel. It has the effect of significantly increasing fluid pressure and reducing flow resistance.

[0027] (3) The heat-conducting heat sink can force the flushing liquid into the end faces of the static ring assembly and the dynamic ring assembly to forcibly take away the heat. At the same time, the heat-conducting heat sink can also conduct heat quickly to ensure that the sealing heat is taken away in time, and a stable and reliable liquid film can be formed on the end faces. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0029] Figure 1 It is a structural schematic diagram of an embodiment;

[0030] Figure 2 is a cross-sectional view of an embodiment;

[0031] Figure 3 This is a structural view of the pumping ring.

[0032] Figure numerals: 1. gland; 2. stationary ring assembly; 3. rotating shaft; 4. pumping ring; 5. moving ring assembly; 6. flushing liquid inlet; 7. flushing liquid outlet; 8. inner cavity; 9. pumping cavity; 10. blocking bump; 11. flushing liquid inlet; 12. guide heat sink; 13. flow gap; 14. flow groove; 15. arc surface; 16. pumping groove. DETAILED DESCRIPTION

[0033] The present invention is further described in detail below in conjunction with the accompanying drawings.

[0034] like Figure 1 , 2 As shown, a high-efficiency circulating cooling device for mechanical seal includes a gland 1, a stationary ring assembly 2 installed on the gland 1, a dynamic ring assembly 5 rotating with a rotating shaft 3, and a pumping ring 4 rotating with the dynamic ring assembly 5, wherein the dynamic ring assembly 5 cooperates with the stationary ring assembly 2 to form a mechanical seal. A flushing liquid inlet 6 and a flushing liquid outlet 7 are provided on the pressure cover 1, an inner cavity 8 is formed between the pressure cover 1, the dynamic ring assembly and the stationary ring assembly 2, the flushing liquid inlet 6 is connected with the inner cavity 8, a pumping cavity 9 is formed between the pumping ring 4 and the pressure cover 1, a blocking protrusion 10 is provided on the pressure cover 1, the blocking protrusion 10 is located in the pumping cavity 9, the flushing liquid outlet 7 is connected with the pumping cavity 9, wherein the blocking protrusion 10 is provided with an arc surface 15 facing the flushing liquid outlet 7, and the connecting point between the flushing liquid outlet 7 and the pumping cavity 9 is located on the arc surface 15, a pumping groove 16 is provided on the pumping ring 4 facing the pumping cavity 9, the inner cavity 8 and the pumping cavity 9 are connected through the flushing liquid inlet 11, the connecting point between the inner cavity 8 and the pumping cavity 9 is located on one side of the blocking protrusion 10, and the connection point between the flushing liquid outlet 7 and the pumping cavity 9 is located on the other side of the blocking protrusion 10.

[0035] During use, relative movement is generated between the dynamic ring assembly 5 and the stationary ring assembly 2. At this time, the friction ring of the dynamic ring assembly 5 and the friction ring of the stationary ring assembly 2 will rub against each other to generate a large amount of heat. At this time, flushing liquid is introduced from the flushing liquid inlet 6. After entering the inner cavity 8, the flushing liquid will contact the dynamic ring assembly 5 and the stationary ring assembly 2, so that the heat generated by the friction between the two is absorbed by the flushing liquid. After absorbing the heat, the flushing liquid will enter the pumping cavity 9 from the flushing liquid inlet 11. Driven by the pumping ring 4, the flushing liquid that has absorbed the heat will flow out from the flushing liquid outlet 7.

[0036] Among them, a guide heat sink 12 is arranged on the pressure cover 1, and the guide heat sink 12 is located in the inner cavity 8 and is arranged around the inner cavity 8. The guide heat sink 12 is located between the flushing liquid inlet 6 and the pumping ring 4. A flow gap 13 for the flushing liquid to pass through is formed between the guide heat sink 12 and the friction ring of the dynamic ring assembly 5. The width of the flow gap 13 is not less than 2.5 mm, and the thermal conductivity of the guide heat sink 12 is greater than the thermal conductivity of the pressure cover 1.

[0037] The flushing liquid entering the inner cavity 8 from the flushing liquid inlet 6 will be forced to be guided between the dynamic ring assembly 5 and the static ring assembly 2 under the action of the guide heat sink 12, so that the heat generated between the dynamic ring assembly 5 and the static ring assembly 2 is taken away in time, ensuring that the sealing heat is taken away in time, and a stable and reliable liquid film can be formed at the sealing end face.

[0038] After a large number of tests and verifications, when the flow gap 13 is less than 2.5 mm, the flow rate of the flushing liquid will decrease sharply, affecting the circulation of the entire flushing liquid, resulting in a large amount of heat remaining in the inner cavity 8, and ultimately affecting the normal operation of the mechanical seal and the service life of the mechanical seal. Therefore, the flow gap 13 is set to a width of not less than 2.5 mm. During operation, the guide heat sink 12 will absorb the heat emitted by the dynamic ring assembly 5 and the static ring assembly 2, and then transfer it to the gland 1, and then dissipate it to the outside world. Due to the high thermal conductivity of the guide heat sink 12, it has a stronger ability to transfer heat, making it easier for the dynamic ring assembly 5 and the static ring assembly 2 to transfer heat to the gland 1.

[0039] like Figure 1 , 3 As shown, the cross section of the pumping groove 16 along the axial direction perpendicular to the pumping ring 4 is an arc groove, and the cross section of the pumping groove 16 along the axial direction passing through the pumping ring 4 is an arc groove, and the ratio of the width of the pumping groove 16 to the distance between two adjacent pumping grooves 16 is 2 / 5~2 / 3. The structure of the pumping groove 16 of this shape is "double arc". Through a large number of experiments, it is verified that the pumping groove 16 of this shape is the best structure. Under the same size, the flow rate is 2~3 times that of the pumping groove 16 of other structures, which can greatly improve the pumping effect of the pumping ring 4 and greatly increase the flow rate of the flushing liquid in the inner cavity 8 and the pumping cavity 9, so that the flushing liquid can take away more heat in the same time. After a large number of experiments, it is verified that when the ratio of the width of the pumping groove 16 to the distance between two adjacent pumping grooves 16 is 2 / 5~2 / 3, the pumping effect of the pumping ring 4 is the best.

[0040] Among them, the inner cavity 8 is an annular cavity, the angle between the flushing liquid inlet 11 and the flushing liquid inlet 6 is 130~160 degrees, the angle between the diameter of the inner cavity 8 and the central axis of the flushing liquid inlet 6 is a, and the angle between the diameter of the inner cavity 8 and the central axis of the flushing liquid outlet 7 is b, the angle a and the angle b are both acute angles, the angle c between the speed direction of the flushing liquid entering the flushing liquid inlet 6 and the speed direction of the flushing liquid in the pumping chamber 9 is an acute angle, and the angle d between the speed direction of the flushing liquid in the flushing liquid outlet 7 and the speed direction of the flushing liquid in the pumping chamber 9 is an acute angle.

[0041] A flow groove 14 is provided on the gland 1, and the pumping ring 4 is located at the opening of the flow groove 14, and the pumping groove 16 faces the flow groove 14. A pumping chamber 9 is formed between the pumping ring 4 and the flow groove 14. The flushing liquid entering the pumping chamber 9 from the flushing liquid inlet 11 flows out from the flushing liquid outlet 7 along the pumping chamber 9. The depth of the flow groove 14 gradually deepens from the flushing liquid inlet 11 to the flushing liquid outlet 7 along the flow direction of the flushing liquid. The shape of the flow groove 14 is a spiral volute shape, which is optimized and improved on the ordinary flow channel. It adopts an eccentric circle and is processed in several sections. Its gradual changeability must be ensured, and it has a significant fluid pressurization effect and reduces flow resistance.

[0042] During use, the flushing liquid is introduced into the inner cavity 8 from the flushing liquid inlet 6. At this time, under the action of the guide heat sink 12, the flushing liquid is forced to be guided between the dynamic ring assembly 5 and the static ring assembly 2. At this time, the flushing liquid will contact the dynamic ring assembly 5 and the static ring assembly 2, and take away the heat generated by the friction between the two. The flushing liquid after absorbing the heat will enter the pumping cavity 9 from the flushing liquid inlet 11. Driven by the pumping ring 4, the flushing liquid that has absorbed the heat will flow out from the flushing liquid outlet 7. Since the pumping effect of the pumping ring 4 is good, the pumping cavity 9 will draw flushing liquid from the inner cavity 8 through the flushing liquid inlet 11, so that the flow rate of the flushing liquid in the inner cavity 8 becomes faster, thereby increasing the heat dissipation effect.

[0043] The above description is merely an exemplary embodiment of the present invention and is not intended to limit the protection scope of the present invention. The protection scope of the present invention is determined by the appended claims.

Claims

1. A high-efficiency circulating cooling device for mechanical seal, comprising a gland (1), a stationary ring assembly (2) mounted on the gland (1), a dynamic ring assembly (5) rotating with a rotating shaft (3), and a pumping ring (4) rotating with the dynamic ring assembly (5), wherein the dynamic ring assembly (5) cooperates with the stationary ring assembly (2) to form a mechanical seal, the gland (1) is provided with a flushing liquid inlet (6) and a flushing liquid outlet (7), an inner cavity (8) is formed between the gland (1) and the dynamic ring assembly and the stationary ring assembly (2), the flushing liquid inlet (6) is in communication with the inner cavity (8), the pumping ring (4) and the gland ( 1), a pumping chamber (9) is formed between the pressure cover (1), a blocking protrusion (10) is provided on the pressure cover (1), the blocking protrusion (10) is located in the pumping chamber (9), the flushing liquid outlet (7) is connected to the pumping chamber (9), the pumping ring (4) is provided with a pumping groove (16) facing the pumping chamber (9), the inner chamber (8) and the pumping chamber (9) are connected through a flushing liquid inlet (11), the connection point between the inner chamber (8) and the pumping chamber (9) is located on one side of the blocking protrusion (10), and the connection point between the flushing liquid outlet (7) and the pumping chamber (9) is located on the other side of the blocking protrusion (10), characterized in that: The gland (1) is provided with a guide heat sink (12) for guiding the flushing liquid entering through the flushing liquid inlet (6) to the mating end surfaces of the stationary ring assembly (2) and the dynamic ring assembly (5); the guide heat sink (12) is located in the inner cavity (8) and is arranged around the inner cavity (8); the guide heat sink (12) is located between the flushing liquid inlet (6) and the pumping ring (4); and a flow gap (13) for the flushing liquid to pass through is formed between the guide heat sink (12) and the friction ring of the dynamic ring assembly (5); The blocking protrusion (10) is provided with a curved surface (15) on the side facing the flushing liquid outlet (7), and the connection point between the flushing liquid outlet (7) and the pumping chamber (9) is located on the curved surface (15); The cross section of the pumping groove (16) along the direction perpendicular to the axis of the pumping ring (4) is an arc-shaped groove, and the cross section of the pumping groove (16) along the direction passing through the axis of the pumping ring (4) is an arc-shaped groove; The pressure cover (1) is provided with a flow groove (14), the pumping ring (4) is located at the opening of the flow groove (14), and the pumping groove (16) faces the flow groove (14), and the pumping chamber (9) is formed between the pumping ring (4) and the flow groove (14). The flushing liquid entering the pumping chamber (9) from the flushing liquid inlet (11) flows out from the flushing liquid outlet (7) along the pumping chamber (9), and the depth of the flow groove (14) gradually increases from the flushing liquid inlet (11) to the flushing liquid outlet (7) along the flow direction of the flushing liquid.

2. The high-efficiency circulating cooling device for mechanical seal according to claim 1 is characterized in that: The width of the flow gap (13) is not less than 2.5 mm.

3. The high-efficiency circulating cooling device for mechanical seal according to claim 1, characterized in that: The thermal conductivity of the guide heat sink (12) is greater than the thermal conductivity of the pressure cover (1).

4. The high-efficiency circulating cooling device for mechanical seal according to claim 1 is characterized in that: The ratio of the width of the pumping groove (16) to the distance between two adjacent pumping grooves (16) is 3 / 2 to 5 / 2.

5. The high-efficiency circulating cooling device for mechanical seal according to claim 1 is characterized in that: The inner cavity (8) is an annular cavity, the angle between the diameter of the inner cavity (8) and the central axis of the flushing liquid inlet (6) is a, the angle between the diameter of the inner cavity (8) and the central axis of the flushing liquid outlet (7) is b, the angle a and the angle b are both acute angles, the angle c between the speed direction of the flushing liquid entering the flushing liquid inlet (6) and the speed direction of the flushing liquid in the pumping cavity (9) is an acute angle, and the angle d between the speed direction of the flushing liquid in the flushing liquid outlet (7) and the speed direction of the flushing liquid in the pumping cavity (9) is an acute angle.

6. The high-efficiency circulating cooling device for mechanical seal according to claim 1 is characterized in that: The angle between the flushing liquid inlet (11) and the flushing liquid inlet (6) is 130 to 160 degrees.

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