A pump shaft seal heat dissipation system

Abstract

The present application relates to a kind of pump shaft seal heat dissipation system, the heat dissipation system includes the second rotor shaft sleeve inner circulation channel, the second rotor shaft sleeve outer circulation channel, pump cover circulation channel and corresponding first rotor shaft sleeve outer circulation channel and first rotor inner circulation channel, the heat dissipation system is circulated in the way in channel by the medium pumped in, and it plays the role of heat dissipation to sealing ring.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of pumps, in particular to a pump shaft sealing heat dissipation system. BACKGROUND

[0002] The cam pump belongs to a kind of rotor pump, it is a kind of rotary positive displacement pump, with the nature of positive displacement, flow does not change with back pressure variation, the relative movement between rotor and pump cavity is changed to work volume size, to medium work in turn.

[0003] The existing double-rotor cam pump generally includes pump cover, pump cavity, main rotor, secondary rotor, synchronous gear, seal, shaft sleeve, bearing and bearing end cover, the main rotor and the secondary rotor are installed in the pump cavity, and the pump cavity is fixedly installed on the bearing cover.The existing double-rotor cam pump, the two rotor rotation radii are consistent, and the efficiency is low.When high-lift medium needs to be transported, in order to improve working pressure, the volume of pump is generally increased, and the volume efficiency is low, the performance is unstable, and the transportation is difficult, and the like.In the prior art, the rotor pump is generally not more than 2MPa, and high pressure and high speed bring large heat, which can quickly damage the sealing element, so how to solve the heat dissipation of the sealing element is an important guarantee for normal work of high pressure and high speed. SUMMARY

[0004] In order to solve the technical problems in the background art, the present application provides the following technical solutions:

[0005] A pump shaft sealing heat dissipation system, the heat dissipation system includes second rotor shaft sleeve inner circulation channel, second rotor shaft sleeve outer circulation channel, pump cover circulation channel, and corresponding first rotor shaft sleeve outer circulation channel and first rotor inner circulation channel, the heat dissipation system is circulated in the channel by the medium transported by the pump, and the sealing ring is heat dissipated.

[0006] An optional embodiment, wherein the pump cover circulation channel is provided with a plurality of transverse V-shaped channels or U-shaped channels in the direction close to the sealing ring.

[0007] An optional embodiment, wherein the second rotor shaft sleeve inner circulation channel includes first circulation heat exchange system and second circulation heat exchange system.

[0008] An optional embodiment, wherein the first circulation heat exchange system medium flow direction is: rotor high-pressure interval gap-outer flow-limiting groove (high-pressure area)-end face annular groove-outer flow-limiting groove (low-pressure area)-rotor low-pressure interval gap.

[0009] An optional embodiment, wherein the flow direction of the second circulating heat exchange system water is specifically: rotor high-pressure interval gap-outer flow-limiting groove (high-pressure zone)-end face annular groove-inner flow-limiting groove (high-pressure zone)-conductive groove (high-pressure zone)-inner annular groove-conductive groove (low-pressure zone)-inner flow-limiting groove (low-pressure zone)-outer flow-limiting groove (low-pressure zone)-rotor low-pressure interval gap.

[0010] An optional embodiment, wherein a third circulating heat exchange system is further included, and the third circulating heat exchange system is based on the second circulating heat exchange system, and the medium is communicated with the second rotor shaft sleeve outer circulating channel through the conductive hole of the inner annular groove, and the medium flow direction specifically includes: conductive hole (high-pressure zone)-second rotor shaft sleeve outer circulating channel-pump cover circulating channel-first rotor shaft sleeve outer circulating channel-conductive hole (low-pressure zone).

[0011] An optional embodiment, wherein the flow direction of the medium in the first circulating heat exchange system, the second circulating heat exchange system and the third circulating heat exchange system changes cyclically with the high-pressure zone and the low-pressure zone.

[0012] A sealing shaft sleeve for the pump shaft sealing heat dissipation system, wherein the sealing shaft sleeve includes a hollow cylindrical shaft sleeve body, the shaft sleeve body includes a first step and a second step and an inner annular groove therebetween, a plurality of conductive grooves are formed on the first step in the axial direction, and the conductive grooves are communicated with the flow-limiting grooves of the shaft sleeve end face.

[0013] An optional embodiment, wherein the shaft sleeve end face is provided with an end face annular groove, and the flow-limiting grooves include a plurality of outer flow-limiting grooves and inner flow-limiting grooves, and the outer flow-limiting grooves and the inner flow-limiting grooves are communicated with the end face annular groove.

[0014] An optional embodiment, wherein the inner annular groove is provided with a plurality of heat dissipation grooves, and the heat dissipation grooves are arranged in the annular direction or are also arranged in the annular direction in an S shape. BRIEF DESCRIPTION OF DRAWINGS

[0015] Figure 1 It is a whole schematic diagram of the volumetric pump of the present application;

[0016] Figure 2 It is a specific schematic diagram of the pump of the present application;

[0017] Figure 3 It is another specific schematic diagram of the pump of the present application;

[0018] Figure 4 It is a specific schematic diagram of the pump cavity of the present application;

[0019] Figure 5 It is a schematic diagram of the first rotor and the second rotor of the present application;

[0020] Figure 6 It is a schematic diagram of the first rotor cam of the present application;

[0021] Figure 7 The second rotor cam schematic diagram of the present application;

[0022] Figure 8 The first rotor and the second rotor cooperation schematic diagram of the present application;

[0023] Figure 9 The first rotor and the second rotor cooperation schematic diagram of the present application;

[0024] Figure 10 The first rotor and the second rotor cooperation schematic diagram of the present application;

[0025] Figure 11 The pump cavity three-dimensional schematic diagram of the present application;

[0026] Figure 12 The pump cavity local three-dimensional schematic diagram of the present application;

[0027] Figure 13 The pump cavity fish mouth local three-dimensional schematic diagram of the present application;

[0028] Figure 14 The fish mouth local three-dimensional schematic diagram of the present application;

[0029] Figures 15-18 The pump working state schematic diagram of the present application;

[0030] Figure 19 The pump heat dissipation system schematic diagram of the present application;

[0031] Figure 20 The pump heat dissipation system local schematic diagram of the present application;

[0032] Figure 21 The pump sealing shaft sleeve schematic diagram of the present application;

[0033] Figure 22 The pump sealing shaft sleeve schematic diagram of the present application; DETAILED DESCRIPTION

[0034] In order to make the purpose, technical scheme and advantages of the present application more clear, the present application is further described in detail below by combining with the drawings and examples. It should be understood that the specific examples described herein are only used to explain the present application, and are not used to limit the present application, that is, the described examples are only a part of the examples of the present application, but not all the examples. The components of the present application described and shown in the drawings herein can be arranged and designed in various different configurations.

[0035] Therefore, the following detailed description of the embodiments of the application provided in the accompanying drawings is not intended to limit the scope of the application claimed, but merely represents selected embodiments of the application. Based on the embodiments of the application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of the application.

[0036] All features disclosed in this specification, or all steps of any methods or processes disclosed, can be combined in any combination, except combinations where at least some of the features, steps or groups thereof would be mutually exclusive.

[0037] The application will be further described below in conjunction with the drawings and specific embodiments:

[0038] Embodiment 1

[0039] In order to solve the problems related to the background art, the present embodiment improves the existing volumetric pump, and the technical solution is as follows:

[0040] A volumetric pump, comprising a pump body 1, the pump body 1 comprising a pump cavity 10 and a first pump cover 105 and a second pump cover 106, the pump cavity 10 and the first pump cover 105 and the second pump cover 106 are connected and fixed, the pump cavity 10 comprises a medium inlet 101 and a medium outlet 102 arranged on both sides, in order to facilitate understanding of the medium inlet 101 and the medium outlet 102 of the present embodiment, the fluid is discharged from right to left, at this time the first rotor 40 rotates clockwise and the second rotor 50 rotates counterclockwise. Define the medium inlet connection area as a low pressure area, and the medium outlet connection area as a high pressure area. An alternative embodiment is that the first rotor 40 rotates counterclockwise and the second rotor 50 rotates clockwise, at this time the positions of the medium inlet 101 and the medium outlet 102 are interchanged. The first rotor 40 is the main rotor, and the first rotor 50 is the auxiliary rotor. When the first rotor 40 and the second rotor 50 rotate in the pump body 1, high pressure areas and low pressure areas are periodically formed in the pump body 1, fluid is sucked by low pressure and is extruded by high pressure, the fluid medium enters the pump cavity 10 from the medium inlet 101, is driven by the first rotor 40 and the second rotor 50, and finally flows from the medium outlet 102 to the outside of the pump body 1 and the external pipeline, completing the normal work of the pump. In an alternative embodiment, the first rotor 40 in the pump cavity has a centerline of rotation higher than the highest point of the medium inlet and outlet by a value in the range of 1mm-30mm.

[0041] The power input end of the first rotor 40 has fan blades, the first rotor 40 and the second rotor 50 are both provided with two bearings and cooling sleeves, the non-driving end of the first rotor 40 and the second rotor 50 are both provided with synchronous gears, and the two are connected through gear transmission. The bearings and high-pressure seals are all mounted on the pump cover, the first rotor 40 and the second rotor 50 are supported and rotated through the bearings at the two ends, the first rotor 40 and the second rotor 50 realize synchronous rotation in opposite directions through a linkage mechanism, and the linkage mechanism includes gear linkage, sprocket linkage and synchronous belt linkage.

[0042] As shown in Figures 1-8 , the first rotor 40 includes a first rotor shaft 401 and a first cam 402, and a cross section perpendicular to the axis of the first rotor shaft 401 is defined as a working cross section. The first cam 402 includes two first main cam surfaces 421 and two second main cam surfaces 422, and in the embodiment, two cam units are provided, and the two cam units are symmetrically arranged along the axis, and in the embodiment, three or more cam units can also be provided. The first main cam surface 421 and the second main cam surface 422 are further provided with a main cam transition surface 423 connected between the two. Figure 9 and Figure 10 , the first main cam surface 421 and the second main cam surface 422 and the main cam transition surface 423 correspond to working curves, that is, the first main cam curve 421a and the second main cam curve 422a and the main cam transition curve 423a directly transitioned therebetween, and the two groups of first main cam curve 421a and second main cam curve 422a and the main cam transition curve 423a therebetween are connected in series to form a first rotor working curve 402a in the working cross section; as Figure 6 and Figure 8 The first main cam curve 421a, the second main cam curve 422a and the main cam transition curve 423a satisfy the following size and angle relationship.

[0043] The first main cam curve 421a satisfies the following curve equation:

[0044]

[0045] The second main cam curve 422a satisfies the following cam equation:

[0046]

[0047] The main cam transition curve 423a satisfies the following transition arc equation:

[0048]

[0049] Wherein:

[0050] r1 is the base circle radius, (r1>r2; r2 mr1+r2

[0051] r2 is a convex circle radius,

[0052] r3 is a transition circle radius,

[0053] r m is a first rotor (main rotor) rotation radius,

[0054] t is a parameter, ranging from 0 to 1;

[0055] θ1 is a base circle included angle, θ1 ranges from 0 to 90°;

[0056] θ2 is a convex circle included angle,

[0057] θ3 is a transition circle included angle, θ3 = θ1 + θ1 - 90°;

[0058] As Figures 5-10 , the second rotor 50 includes a second rotor shaft 501 and a second cam 502, the second cam 502 includes two first sub-rotor surfaces 521 and two second sub-rotor surfaces 522, in the embodiment, the cam unit is two, the two cam units are symmetrically arranged along the axis, and three or more cam units can also be arranged. The first sub-rotor surface 521 and the second sub-rotor surface 522 are connected by a sub-rotor transition surface 523. The first sub-rotor surface 521 and the second sub-rotor surface 522 and the sub-rotor transition surface 523 therebetween correspond to the first sub-rotor curve 521a and the second sub-rotor curve 522a and the first sub-rotor transition curve 523a and the second sub-rotor transition curve 524a connected therebetween, the two groups of first sub-rotor curves 521a and second sub-rotor curves 522a connected end to end and the first sub-rotor transition curve 523a and the second sub-rotor transition curve 524a therebetween form a second rotor working curve 502a; the first rotor working curve 402a and the second rotor working curve 502a form a conjugate convex-concave curve. The first sub-rotor curve 521a and the second sub-rotor curve 522a and the first sub-rotor transition curve 523a and the second sub-rotor transition curve 524a satisfy the following size and angle relationship:

[0059] The first sub-rotor curve 521a satisfies the following curve equation:

[0060]

[0061] The second rotor working curve 502a satisfies the following curve equation:

[0062]

[0063] The first sub-rotation transition curve 523a satisfies the following curve equation:

[0064]

[0065] The second sub-rotation transition curve 524a satisfies the following curve equation:

[0066]

[0067] wherein β1 is the included angle between MO1 and O1P,

[0068] t is a parameter, ranging from 0 to 1;

[0069] θ4 is the included angle between the starting point and the ending point of the second sub-rotation curve segment of the first rotor (main rotor) in the coordinate system with the center O1 as the coordinate origin,

[0070] c is the distance from the starting point of the second sub-rotation curve segment of the first rotor (main rotor) to the center O1,

[0071]

[0072] r m is the rotation radius of the first rotor (main rotor); r1 is the base circle radius; and r2 is the convex circle radius;

[0073] η is the included angle between PO2 and O1O2,

[0074] r3 is the transition arc radius,

[0075] θ1 is the base circle included angle;

[0076] θ3 is the transition included angle, θ3 = θ1 + θ2 - 90°;

[0077] θ2 is the convex circle included angle,

[0078] O3P is the length of the center O3 and the conjugate instant point P,

[0079]

[0080] η5 is the included angle between O3P and O1P,

[0081] O1M is the length of the center O1 and the conjugate point M,

[0082]

[0083] The skilled in the art should understand that the first sub-rotation curve 521a and the second sub-rotation curve 522a extend to form a virtual intersection point D1(not shown), the first sub-rotation curve 521a and the second sub-rotation curve 522a form an intersection point D2(not shown), when the first rotor 40 and the second rotor 50 are matched, a gap mutation occurs at the intersection point D1and the intersection point D2, causing the high pressure area to be decompressed, thereby greatly affecting the efficiency of the volumetric pump.

[0084] In the embodiment, the first main rotation curve 421a and the first sub-rotation curve 521a form a conjugate curve

[0085] The second main rotation curve 422a and the second sub-rotation curve 522a form a conjugate curve, and the main rotation transition curve 423a and the first sub-rotation transition curve 523a and the second sub-rotation transition curve 524a form a conjugate curve. The first rotor 40 and the second rotor 50 can maintain a stable and substantially same gap, especially the transition section also maintains a stable gap, without gap mutation, thereby ensuring the stability of the high pressure area and improving the overall efficiency of the volumetric pump.

[0086] The turning radius r of the first rotor 40 m is greater than the turning radius R2 of the second rotor 50, and the ratio of r m The ratio of r / R2 is in the range of 1.1-2.8.

[0087] The source power is input from the first rotor 40, which mainly plays a main working role in the pump cavity 10, while the second rotor 50 plays an auxiliary working role and mainly plays a good dynamic sealing role.

[0088] Figures 1-4 As shown, the pump cavity 10 is a cavity 120 defined by a first turning line segment 124 of a first cavity turning line 121, a second turning line segment 125 of a second cavity turning line 122, and a tangent line 123 of the two, the first cavity turning line 121 has a radius R10, the second cavity turning line 122 has a radius R20, the gap A is the minimum gap between the first rotor 40 and the first cavity turning line 121 region, and the gap B is the minimum gap between the second rotor 50 and the second cavity turning line 122 region, which satisfies the formula R10=r m +A; R20=R2+B; the gap A≤the gap B, the gap A is in the range of 0.03-0.3mm, and the gap B is in the range of 0.03-0.5mm.

[0089] The first rotor 40 and the second rotor 50 are provided with matching bearings at both ends, the second rotor 50 is driven by a synchronous gear, the first rotor 40 and the second rotor 50 rotate in opposite directions synchronously, the first cam 402 and the second cam 502 are conjugate curves and keep a certain gap, the first rotor working curve 402a and the second rotor working curve 502a form a conjugate convex-concave curve, the gap C is in the range of 0.03-0.3mm. In the preferred embodiment, the conjugate convex-concave curve keeps a substantially same gap.

[0090] In the embodiment, the main rotor transition curve 423a and the auxiliary rotor transition curve 523a are arranged to form a meshing fit, the first rotor working curve 402a and the second rotor working curve 502a keep a substantially same gap, and there is no obvious pressure relief point, so that the pressure in the high pressure area is maintained.

[0091] Those skilled in the art should understand that the first rotor 40 and the second rotor 50 also have a certain gap with the pump cover, so that the first rotor 40 and the second rotor 50 do not rub and interfere with each other when moving, and the gap between the rotor and the pump cover ensures that the rotor does not rub and interfere with the pump cover when moving.

[0092] Those skilled in the art should understand that when the medium to be extracted contains a large amount of impurities or residues, it is easy to cause the volumetric pump to be blocked. For the convenience of understanding, the gap A and the gap B are set to 0, and the first rotor 40 rotates, the vertex of the convex first main rotor surface 421 is in line contact with the first rotary line segment 124 of the pump cavity 10, and the second rotor 50 rotates, the convex first auxiliary rotor surface 521 is in surface contact with the second rotary line segment 125 of the pump cavity 10. Those skilled in the art should understand that when the gap A and the gap B are greater than 0, the vertex of the first main rotor surface 421 is in the minimum gap position with the first rotary line segment 124 when the first rotor 40 rotates, and the minimum gap position is only the vertex corresponding area of the first main rotor surface 421. When the second rotor 50 rotates, the minimum gap position between the first auxiliary rotor surface 521 and the second rotary line segment 125 is the corresponding area of the first auxiliary rotor surface 521. When the pump needs to work at high lift, the cavity pressure can be increased by increasing the rotation speed of the first rotor. Since the second rotor 50 forms a dynamic seal with the second rotary line segment 125, sudden pressure relief can be effectively avoided, and the pressure in the high pressure area is stable.

[0093] The first rotor 40 plays an active role in power generation. Compared to a dual-rotor positive displacement pump of roughly the same size, if a multi-cam unit is used, the diameter of the main rotor usually cannot be designed to be too large in order to ensure the coordination between the cams. In this embodiment, due to the use of asymmetrical rotors, the rotation radius of the first rotor 40 is larger than that of the second rotor 50. The first rotor shaft 401 has room to increase its diameter, which can be thickened to ensure that the first rotor shaft 401 does not break or fail under the high pressure requirements of the positive displacement pump and under the condition of large torque.

[0094] Example 2

[0095] like Figures 11-14 As shown, this embodiment, based on Embodiment 1, provides a detailed description of the pump chamber 10. The pump chamber 10 also includes a fish-mouth 103, which is positioned along the extension direction of the second chamber rotation line 122, at the point of tangency between the second chamber rotation line 122 and the tangent line 123. The fish-mouth 103 includes a fish-mouth mating section 131, a fish-mouth water-dividing section 132, and a fish-mouth tip 133 where the two sections intersect. The fish-mouth mating section 131 of the fish-mouth 103 increases the mating area between the second rotation line segment 125 and the first secondary rotation surface 521 (gap B), effectively improving the dynamic sealing effect. The fish-mouth 103 and the pump chamber 10 can be fixed by an integral molding connection.

[0096] In one optional technical solution, the distance between the fish mouth water-dividing section 132 and the first cavity rotation line 121 is greater than 10mm, and the fish mouth 103 does not interfere with the first rotor 40.

[0097] like Figure 11 As shown, in another optional technical solution, the gap between the fish-mouth mating section 131 and the first auxiliary rotating surface 521 during dynamic sealing is gap B, or a gradual gap can be used. The material of the fish-mouth mating section 131 includes self-lubricating plastics such as POM, PTFE, and PA, or other self-lubricating materials and semi-rigid materials. The fish-mouth 103 and the pump cavity 10 can be bonded, welded, or otherwise fixedly connected. In another optional technical solution, the top end 133 of the fish-mouth protrudes to form a minimum gap between the first fish-mouth adjusting section 134 and the first auxiliary rotating surface 521, with the gap being B1. As the distance from the first fish-mouth adjusting section 134 to the position of the second cavity rotation line 122 increases, the gap between the fish-mouth mating section 131 and the first auxiliary rotating surface 521 gradually increases, and the gap B1 < gap B. Since there is a gap B1 between the fish mouths on both sides of the symmetry, the length of the first secondary rotating surface 521 corresponding to the first secondary rotating curve 521a must satisfy the following: when the second rotor 50 is at any position, the first secondary rotating surface 521 must cooperate with the fish mouth on at least one side with a gap B1, and the gap at other positions can be greater than the gap B1.

[0098] In another alternative, the first rotor shaft 401 of the first rotor 40 and the second rotor shaft 501 of the second rotor 50 are made of metal material, the first cam 402 is made of metal material, and the second cam 502 is made of self-lubricating plastic such as POM, PTFE, PA, etc., which can further reduce the gap between the second rotor 50 and the second cavity revolving line 122 and the fish mouth matching segment 131.

[0099] The volumetric pump in the embodiment can achieve a high lift of more than 200 meters. Compared with the volumetric pump in the prior art under the same working condition, the volume is reduced by 40%, and compared with the centrifugal pump in the prior art under the same lift and flow, the efficiency is increased by more than 20%.

[0100] When the gap B1 is less than the gap B, those skilled in the art should understand that, in order to achieve the same dynamic sealing effect, the gap B can adopt a larger range of values in the case of using a gradually changing gap. This technical solution not only meets the motion sealing performance of the second rotor 50, but also reduces the assembly difficulty and the processing difficulty of the pump cavity 10 (the processing precision requirement of the first secondary rotor face 521 can be reduced). In particular, when the POM material fish mouth 103 is used to extract a large amount of debris, the larger range of values of the gap B can avoid the blockage of the second rotor 50 and effectively reduce the dynamic sealing sliding friction force of the first secondary rotor face 521.

[0101] As shown in Figure 12 In another alternative, the fish mouth matching segment 131 is set as a rotatable roller, and the fish mouth matching segment 131 forms rolling friction with the first secondary rotor face 521 during the dynamic sealing process of the first secondary rotor face 521. Since the friction of rolling friction is smaller, the gap B1 is smaller, thereby further improving the dynamic sealing performance.

[0102] In another embodiment, the fish mouth matching segment 131 is also provided with a second fish mouth adjusting segment 135, and the gap between the second fish mouth adjusting segment 135 and the first secondary rotor face 521 during the dynamic sealing process is B2, and the gap B1 is less than the gap B2 which is less than the gap B. The first fish mouth adjusting segment 134 and the second fish mouth adjusting segment 135 can be set simultaneously or separately, and the fish mouth 103 and the first secondary rotor face 521 form a high-pressure area gradually reduced in pressure during the process of matching the gap. More fish mouth adjusting segments can also be provided on the fish mouth matching segment 131. By using multiple fish mouth adjusting segments, the dynamic sealing performance of the first secondary rotor face 521 can be further improved.

[0103] In another embodiment, the fish mouth 103 is made of rigid material, the first fish mouth adjusting segment 134 and the second fish mouth adjusting segment 135 are made of flexible material, which can further reduce the range of the gap B1 and the gap B2, and further increase the dynamic sealing of the first secondary rotor blade surface 521 without increasing the dynamic sealing sliding friction of the first secondary rotor blade surface 521. The fish mouth adjusting segment is arranged along the axial direction of the second rotor 50, and can also be S-shaped or other shapes that penetrate the axial direction of the fish mouth.

[0104] As shown in Figure 12 In another optional embodiment, the fish mouth 103 further includes a grease storage bag (not shown) that stores lubricating grease, and a plurality of grease discharge holes 136 are arranged in the first fish mouth adjusting segment 134, which is made of flexible material. In this embodiment, the gap B1 between the first fish mouth adjusting segment 134 and the first secondary rotor blade surface 521 can be 0, and the first fish mouth adjusting segment 134 and the first secondary rotor blade surface 521 can also form an interference fit. When the second rotor 50 rotates, the first secondary rotor blade surface 521 extrudes the first fish mouth adjusting segment 134, and the lubricating grease automatically overflows from the grease discharge holes 136 to lubricate the first secondary rotor blade surface 521 and the first fish mouth adjusting segment 134. This embodiment can achieve good dynamic sealing of the first secondary rotor blade surface 521 without increasing the dynamic sealing sliding friction of the first secondary rotor blade surface 521.

[0105] In the case of conveying different media, especially in the case of more impurities, the second rotor 50, which mainly plays a sealing role, may be blocked. In another embodiment, the first fish mouth adjusting segment 134 is movably connected to the fish mouth 103 as a sliding block, the first fish mouth adjusting segment 134 includes an adjusting segment sliding block segment 139, a threaded adjusting rod 137, and an adjusting segment knob 138, the adjusting segment sliding block segment 139 is movably connected to the threaded adjusting rod 137, and the adjusting segment knob 138 is arranged outside the pump cavity 10 and matches an internal threaded hole in the pump cavity 10 at the corresponding position of the threaded adjusting rod 137. Rotating the adjusting segment knob 138, the threaded adjusting rod 137 is fed or withdrawn in the pump cavity 10, the threaded adjusting rod 137 pushes the adjusting segment sliding block segment 139 to protrude into the pump cavity 10 or retract, thereby adjusting the gap between the first fish mouth adjusting segment 134 and the first secondary rotor blade surface 521. During use, the gap B1 between the first fish mouth adjusting segment 134 and the first secondary rotor blade surface 521 on the fish mouth 103 can be adjusted, the gap B1 is increased when the problem of blockage occurs, thereby achieving the effect of slagging, and the gap B1 is reduced after the slagging is completed, thereby achieving dynamic sealing.

[0106] As shown in Figure 13As shown, in another alternative embodiment, the first fish mouth adjusting segment 134 is movably connected to the fish mouth 103 in a slider mode, the first fish mouth adjusting segment 134 comprises an adjusting slider 139a, an elastic adjusting rod 137a and a limiting clamp 138a, the adjusting slider 139a is connected to the elastic adjusting rod 137a, and the limiting clamp 138a is fixed on the pump cavity 10. The first fish mouth adjusting segment 134 is in contact with or maintains a small gap with the first secondary rotor surface 521, when the second rotor 50 rotates, the first fish mouth adjusting segment 134 is compressed by the first secondary rotor surface 521, the first fish mouth adjusting segment 134 is in continuous force contact with the first secondary rotor surface 521, and due to the compression of the elastic adjusting rod 137a, the contact pressure of the first fish mouth adjusting segment 134 is small, but it can achieve good sealing effect.

[0107] As shown in Figure 11 and Figure 14 shown, the pump cavity 10 is replaced by the adjustable fish mouth 103a shown in Figure 14 which can achieve angle adjustment, the adjustable fish mouth 103a is arranged along the downward extension direction of the second cavity rotation line 122 from the intersection position of the second cavity rotation line 122 and the tangent line 123, the adjustable fish mouth 103a comprises a fish mouth body 168, a turbine shaft 163, a turbine 161 and a worm 162 matched therewith, the fish mouth body 168 is provided with a fish mouth arc body 165, and the fish mouth body 168 is provided with a sealing groove 166 and a U-shaped mounting groove 169, the sealing groove 166 is provided with a sealing strip to form a seal with the pump cavity 10. The turbine shaft 163 is fixed with the turbine 161 and the fish mouth body 168, and the pump cavity 10 is provided with a mounting table 167 for assembling the U-shaped mounting groove 169. The mounting table 167 and the U-shaped mounting groove 169 are rotatably movably connected through the turbine shaft 163. The worm 162 extends out of the pump cavity 10 to provide a handle 164. Rotating the handle 164 of the worm 162 drives the fish mouth body 168 to rotate, thereby adjusting the gap size during the dynamic sealing process of the fish mouth arc body 165 and the first secondary rotor surface 521. On the one hand, during the angle adjustment process, the sealing strip or sealing film of the sealing groove 166 needs to be compressed, and after the sealing strip is compressed, a certain compression reaction force will be generated, especially during the high-speed rotation of the second rotor 50, the fish mouth body 168 will also bear a large force, thereby causing the risk of automatic rotation of the adjustable fish mouth 103a and causing failure, however, through the cooperation of the turbine 161 and the worm 162 to form a self-locking effect, it is ensured that the adjustable fish mouth 103a does not rotate after the angle is adjusted, and the angle is fixed. This embodiment can adjust the angle of the adjustable angle fish mouth 103a according to actual needs, and improve the dynamic sealing performance and slag discharge effect of the second rotor 50.

[0108] As shown in Figures 15-18As shown, the embodiment describes in detail that when the first rotor 40 and the second rotor 50 rotate in the pump body 1, high pressure areas and low pressure areas are periodically formed in the pump body 1, the pump uses low pressure to suck fluid and uses high pressure to extrude fluid, the fluid medium enters the pump cavity 10 from the medium inlet 101, is driven by the first rotor 40 and the second rotor 50, and finally flows to the outside of the pump body 1 from the medium outlet 102, and the fluid medium is finally discharged from the pump body 1 to the external pipeline, thereby completing the normal work of the pump.

[0109] Embodiment 3

[0110] Those skilled in the art should understand that the current rotor pump is generally not more than 2 MPa, because high pressure and high speed will cause large heat and quickly damage the seal, therefore, how to solve the heat dissipation of the seal is an important guarantee for ensuring the normal work of high pressure and high speed. For example, the seal of the pump is shown in the following figure: Figures 19-22 As shown, the embodiment describes in detail the shaft seal heat dissipation system based on the embodiments 1 and 2. The first pump cover 105 is connected to the pump cavity 10 by bolts and nuts, the bearing 605 is installed on the second rotor shaft 501 by transition fit, the sealing pressure plate 603 is tightly attached to the bearing 605, and the inner V curved surface of the irregular π type skeleton seal 604 is tightly attached to the second rotor shaft 501. The irregular π type skeleton seal 604 and the sealing pressure plate 603 form a heat dissipation circulation loop and are tightly pressed against the end surface of the sealing shaft sleeve 60, and the sealing shaft sleeve 60 is installed on the second rotor shaft 501. The sealing ring 602 is installed on the sealing shaft sleeve 60, and the sealing ring 602 is a double-layer sealing ring including an O type rubber sealing ring one 621 and an O type rubber sealing ring two 622.

[0111] The skilled in the art should understand that the main reason for the failure of the sealing heat is that the sealing ring 602 is overheated during the high-speed rotation of the second rotor 50, which causes the failure of the sealing ring 602. The shaft sealing heat dissipation system of the embodiment adopts a medium automatic circulation mode formed by the pump to form a heat dissipation system. In order to facilitate understanding, one side of the second rotor 50 is described in the embodiment, and the other side of the second rotor 50 is basically a symmetrical structure; specifically including the second rotor shaft sleeve inner circulation channel 631, the second rotor shaft sleeve outer circulation channel 632 formed by the sealing pressure plate 603, the sealing ring 602 and the first pump cover 105, the pump cover circulation channel 633, and the corresponding first rotor shaft sleeve outer circulation channel 634 and first rotor inner circulation channel (basically the same as the second rotor shaft sleeve inner circulation channel 631). The pump cover circulation channel 633 connects the second rotor shaft sleeve outer circulation channel 632 and the first rotor shaft sleeve outer circulation channel 634. In the embodiment, the pump cover circulation channel 633 is arranged on the first pump cover 105, and a plurality of transverse V-shaped channels are arranged in the pump cover circulation channel 633 in the direction close to the sealing ring 602. The pump cover circulation channel 633 can also be arranged as a transverse U-shaped channel or other shapes. The pump cover circulation channel 633 plays a cooling role in the heat dissipation of the outer ring surface of the sealing ring 602. The first rotor shaft sleeve outer circulation channel 634 plays a cooling role in the heat dissipation of the side surface of the sealing ring 602.

[0112] The sealing bush 60 comprises a hollow cylindrical bush body 600 made of a material with good heat conduction, including brass, bronze or stainless steel. The bush body 600 comprises a bush end face 601 matched with the second rotor 50, the bush body 600 comprises a first step 616, a second step 617 and an inner annular groove 614 therebetween, a plurality of through grooves 613 are formed on the first step 616 in the axial direction, the bush end face 601 is provided with an end face annular groove 615, and an outer flow limiting groove 611 and an inner flow limiting groove 612 are arranged on the bush end face 601 at positions corresponding to the through grooves 613, the outer flow limiting groove 611 and the inner flow limiting groove 612 are in communication with the end face annular groove 615, and the inner flow limiting groove 612 is in communication with the end face annular groove 615. A through hole 610 is formed on the inner annular groove 614. The end face annular groove 615 is mainly used for cooling the bush end face 601 and then cooling the side of the sealing ring 602 close to the bush end face 601. The inner annular groove 614 is arranged at a position corresponding to the mounting position 614a of the sealing ring 602 on the outer surface of the bush body 600, and the cooling medium indirectly cools the inner annular surface of the sealing ring 602 through the mounting position 614a on the outer surface of the bush body 600. In an optional embodiment, the outer flow limiting groove 611 and the inner flow limiting groove 612 are arranged in two groups in the axial direction. In another optional embodiment, a plurality of heat dissipation grooves 614b are arranged in the inner annular groove 614, which can effectively increase the heat dissipation area of the inner annular groove 614, and the heat dissipation grooves 614b can be arranged in the annular direction or in the annular S-shaped direction.

[0113] In combination Figures 19-22 , in this embodiment, the medium fluid is taken as water for example. Since there is a gap between the first pump cover 105 and the first rotor 40 and between the second pump cover 106 and the second rotor 50, and the cavity has a cyclic change of high pressure area and low pressure area, the medium fluid in the high pressure area can communicate with the outer flow limiting groove 611 through the gap, and the two symmetrical outer flow limiting grooves 611 are in the high pressure area and the low pressure area when the second rotor 50 rotates. Water forms a first circulating heat exchange system in the end face annular groove 615, and the flow direction of water is: rotor high pressure area gap-outer flow limiting groove 611 (high pressure area)-end face annular groove 615-outer flow limiting groove 611 (low pressure area)-rotor low pressure area gap.

[0114] The flow direction of water in the second circulating heat exchange system is: rotor high pressure area gap-outer flow limiting groove 611 (high pressure area)-end face annular groove 615-inner flow limiting groove 612 (high pressure area)-through groove 613 (high pressure area)-inner annular groove 614-through groove 613 (low pressure area)-inner flow limiting groove 612 (low pressure area)-outer flow limiting groove 611 (low pressure area)-rotor low pressure area gap.

[0115] The third circulation heat exchange system is based on the second circulation heat exchange system, and the water is communicated with the second rotor shaft sleeve outer circulation channel 632 through the through hole 610 of the inner annular groove 614. The flow direction of the water specifically includes: the through hole 610 (high pressure area)-the second rotor shaft sleeve outer circulation channel 632-the pump cover circulation channel 633-the first rotor shaft sleeve outer circulation channel 634-the through hole 610 (low pressure area, the corresponding position of the first rotor shaft sleeve).

[0116] The first circulation heat exchange system and the second circulation heat exchange system form the second rotor shaft sleeve inner circulation channel 631, which mainly indirectly cools and lowers the temperature of the inner annular surface of the sealing ring 602 through the sealing shaft sleeve 60. The second rotor shaft sleeve outer circulation channel 632 and the first rotor shaft sleeve outer circulation channel 634 in the third circulation heat exchange system mainly directly cool and lower the temperature of the side surface of the sealing ring 602, and the pump cover circulation channel 633 mainly cools and lowers the temperature of the outer annular surface of the sealing shaft sleeve 60 through the pump cover. The inner annular surface, the outer annular surface and the side surface of the sealing ring 602 are directly or indirectly cooled through the first circulation heat exchange system, the second circulation heat exchange system and the third circulation heat exchange system, so that the sealing ring 602 can maintain a normal working state and will not have a significant temperature rise.

[0117] Those skilled in the art should understand that, since the first rotor 40 and the second rotor 50 are in operation, the high pressure area and the low pressure area are cyclically changed, and the flow direction of the liquid in the first circulation heat exchange system, the second circulation heat exchange system and the third circulation heat exchange system is also cyclically changed.

[0118] An optional embodiment is provided in the third circulation heat exchange system, in which a driving motor and an impeller are arranged in the pump cover circulation channel 633, and the liquid in the pump cover circulation channel 633 is directly driven by the impeller. In particular, for fluid media with poor flowability, such as oily media, the liquid flow speed in the third circulation heat exchange system can be effectively improved, and the heat exchange efficiency can be improved.

[0119] Those skilled in the art should understand that the shaft sealing heat dissipation system of the present embodiment can be used in the embodiments 1 or 2 of the present application, or can be used in the shaft sealing heat dissipation of the prior art, and can be used in a volumetric pump or other prior art pumps.

[0120] The above merely describes a preferred embodiment of the present application, but the protection scope of the present application is not limited thereto, any person skilled in the art can make equivalent replacements or changes to the technical scheme and inventive concept of the present application within the technical scope disclosed by the present application, which should be covered within the protection scope of the present application. In the description of the present application, it should be noted that the orientation or position relationship indicated by the terms "top", "bottom", "one side", "the other side", "front", "back", "intermediate position", "interior", "top end", "bottom end" and the like is based on the orientation or position relationship shown in the drawings, and is merely for the convenience of describing the present application and simplifying the description, and is not intended to indicate or imply that the device or element referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as a limitation on the present application; the terms "first", "second", "third" are merely for the purpose of description, and cannot be understood as indicating or implying relative importance; in addition, unless otherwise explicitly specified and limited, the terms "mounting", "connection", "connecting" should be understood broadly, for example, can be fixed connection, can also be detachable connection or movable connection, or integral connection; can be mechanical connection, can also be electrical connection; can be direct connection, can also be indirect connection through an intermediate medium, can be the communication inside two elements. For the person skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

Claims

1. A pump shaft seal heat dissipation system characterized by: The pump body comprises a pump cavity and a pump cover, the heat dissipation system comprises a second rotor shaft sleeve inner circulation channel, a second rotor shaft sleeve outer circulation channel, a pump cover circulation channel, and a first rotor shaft sleeve outer circulation channel and a first rotor inner circulation channel, the heat dissipation system is circulated in the channel by the medium pumped by the pump, the heat dissipation system plays a heat dissipation role on the sealing ring, the pump cavity further comprises a fish mouth formed in the natural extension direction of the second cavity rotation line, and the fish mouth is provided with at least one fish mouth adjusting section in the gap B matching area.

2. The pump shaft seal heat dissipation system of claim 1, wherein, The pump cover circulation channel is provided with a plurality of transverse V-shaped channels or U-shaped channels in the direction close to the sealing ring.

3. The pump shaft seal heat dissipation system of claim 1, wherein, The second rotor shaft sleeve inner circulation channel comprises a first circulation heat exchange system and a second circulation heat exchange system.

4. The pump shaft seal heat dissipation system of claim 1, wherein, The medium flow direction of the first circulation heat exchange system is: rotor high-pressure interval gap-high-pressure outer limiting groove-end surface annular groove-low-pressure outer limiting groove-rotor low-pressure interval gap.

5. The pump shaft seal heat dissipation system of claim 1, wherein, The water flow direction of the second circulation heat exchange system is: rotor high-pressure interval gap-outer limiting groove high-pressure area-end surface annular groove-high-pressure inner limiting groove-high-pressure area guide groove-inner annular groove-low-pressure area guide groove-low-pressure inner limiting groove-low-pressure outer limiting groove-rotor low-pressure interval gap.

6. The pump shaft seal heat dissipation system of claim 3, wherein, The third circulation heat exchange system is further included, the third circulation heat exchange system is connected with the second rotor shaft sleeve outer circulation channel through the guide hole of the inner annular groove based on the second circulation heat exchange system, and the medium flow direction comprises: high-pressure area guide hole-second rotor shaft sleeve outer circulation channel-pump cover circulation channel-first rotor shaft sleeve outer circulation channel-low-pressure area guide hole.

7. The pump shaft seal heat dissipation system of claim 6, wherein, The medium flow direction of the first circulation heat exchange system, the second circulation heat exchange system and the third circulation heat exchange system changes cyclically with the change of the high-pressure area and the low-pressure area.

8. A seal bushing for use in the pump shaft seal heat dissipation system of any of claims 1-7, wherein, The sealing shaft sleeve comprises a hollow cylindrical shaft sleeve body, the shaft sleeve body comprises a first step and a second step and an inner annular groove between the first step and the second step, a plurality of guide grooves are formed on the first step in the axial direction, and the guide grooves are communicated with the limiting grooves on the shaft sleeve end face.

9. The bushing of claim 8, wherein, The shaft sleeve end face is provided with an end surface annular groove, the limiting grooves comprise a plurality of outer limiting grooves and inner limiting grooves, and the outer limiting grooves and the inner limiting grooves are communicated with the end surface annular groove.

10. The bushing of claim 8, wherein, The inner annular groove is provided with a plurality of heat dissipation grooves, and the heat dissipation grooves are arranged in the annular direction or are also arranged in the S-shaped annular direction.

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