CN112012931A

CN112012931A - Cooling design of pump rotor

Info

Publication number: CN112012931A
Application number: CN202010920302.6A
Authority: CN
Inventors: 李军
Original assignee: Zhejiang Cisco Vacuum Technology Co ltd
Current assignee: Zhejiang Cisco Vacuum Technology Co ltd
Priority date: 2020-09-04
Filing date: 2020-09-04
Publication date: 2020-12-01
Anticipated expiration: 2040-09-04
Also published as: CN112012931B

Abstract

The invention discloses a cooling design of a pump rotor, belongs to the technical field of pump rotor cooling, and aims to solve the problem of heat conduction of the rotor after acting, cool the rotor, reduce the heat conducted along a rotor shaft, and reduce the temperature of a bearing and a sealing part. One or two equidistant spiral spring-like components, a base capable of fixing the spring-like components, a shaft sleeve and a thin-wall pipe are arranged in the rotor. When two holes formed in the shaft sleeve are respectively arranged at two sealed space positions, and a cooling medium is filled in the sealed outer hole position space, wherein the cooling medium can be liquid or gas. When the rotor rotates, the pumping effect is realized by the spring-like component in the thin-wall pipe, and the cooling medium is introduced into the inner and outer apertures of the rotor through the thin-wall pipe for heat exchange, so that the process of cooling the rotating rotor is completed. The invention can more effectively realize the purpose of cooling the rotor through the cooling circulation.

Description

Cooling design of pump rotor

Technical Field

The invention belongs to the technical field of pump rotor cooling, and particularly relates to a cooling design of a pump rotor.

Background

In the prior art systems, the heat generated by the work of most equipment with a rotating rotor can cause the temperature of the rotor to rise, especially gas phase conveying equipment, along with the rotation of the rotor, gas enters a pump cavity from a suction inlet, the energy consumed by the rotating rotor is endowed to the gas, so that the gas first acquires kinetic energy, limited by the physical and chemical properties of the gas and the resistance caused by the velocity, the pressure and temperature of the gas will rise synchronously, which will produce compression, and as the difference between the suction port pressure and the discharge pressure increases, the compression power consumption becomes the most dominant energy consumption, in this process, it is well known that, according to the first law of thermodynamics, the energy is finally converted into heat which is absorbed by the gas, and the adiabatic equation well describes the process of this energy conversion, while the gas equation of state describes well the course of changes between pressure, volume and temperature.

The gas containing these heat is transferred to the cryogenic object or medium by means of heat conduction, heat radiation, convection heat transfer, etc. as is well known, according to the second law of thermodynamics, in the case of a screw vacuum pump or a compressor, these heat will be transferred to the pump body and the rotors synchronously by the above-mentioned means, and the pump body can exchange heat by the cooling medium through the sandwich design, while the rotating rotors can only transfer heat axially depending on the thermal properties of the material, although in this process, the heat transferred axially still includes the above-mentioned several heat conduction means, but most rotors are limited in that they can only transfer heat by the shaft and the outside, so that the area for exchanging heat with the outside is limited, and only very little heat can be transferred — this results in that the temperature of the rotors is almost equal to the temperature of the gas after it does work at steady state, at this temperature, the temperature gradient distribution of the heat conducted in the axial direction and the amount of heat transferred are determined by the thermal properties of the material.

It is a well known fact that any rotating rotor must be provided with the necessary support, whether rigid or flexible, to allow the rotor to rotate, and it is common design conditions that for the rotating rotor to operate reliably, bearings are used at the support to reduce its frictional losses and maintain its concentricity requirements, and seals are used to isolate the bearings from the media, thereby ensuring continued reliable operation of the rotating equipment. However, one fact known to those skilled in the relevant art is that temperature, whether it be a bearing or a seal, has a significant effect on its reliability life and oil change cycle, and it follows the law that temperature increases negatively impact its oil change cycle and life.

In addition to the above mentioned effects of heat transfer through axial direction, for those devices that require the rotation of intermeshing rotors to perform work, such as screw vacuum pumps or compressors, roots vacuum pumps or blowers, claw vacuum pumps or compressors, etc., the heat absorbed by the rotors causes them to expand radially and axially, and the temperature gradients determined by the thermal properties of the rotor materials cause deformations that risk interference between these types of rotors. While it is necessary to leave sufficient clearances between these types of rotors and the pump body, and between the rotors and the rotors, in order to cope with the risks of thermal expansion and interference, too large clearances will, however, seriously degrade their performance.

In order to reduce the temperature and avoid or reduce the defects caused by the temperature, a plurality of improvements and designs are made by persons skilled in the relevant field in the prior art:

1. in the granted patent publication No. CN100473838C, a cooling solution for a screw vacuum pump rotor is provided, which introduces a coolant into a cavity established inside the rotor through a hollow shaft on the screw rotor, and a connecting pipe is respectively built inside the hollow shaft and the cavity inside the rotor, so that the coolant enters the coolant from the connecting pipe, and the coolant which has absorbed heat flows out of the connecting pipe, and finally the coolant enters and exits at the end of the shaft, thereby realizing the process of heat exchange between the screw rotor and the gas which does work.

But the disadvantages are: the structure is complicated and the incoming coolant must be under additional pressure to achieve the process of convective heat transfer. And exacting requirements are placed on the accuracy of the machining of these components that make up the convective heat transfer process. In addition to this, the overall design of convective heat transfer to achieve this solution would be very complex.

2. In the granted patent publication No. CN105386972B, a screw vacuum pump with a dynamic seal structure is provided, which forms a cooling channel by establishing an annular cavity structure in the rotor and installing a stationary sandwich member in the annular cavity, and a cooling medium is provided in the cooling channel, thereby isolating part of the rotor from heat transfer radially to the shaft and reducing the heat on the rotor shaft through the cooling channel.

But the disadvantages are: the cooling jacket is complicated to manufacture and its heat transfer depends only on the heat radiation of the rotor for heat exchange, so its cooling effect is very limited. In addition, the rotor of such a structure causes deterioration in stability of rotation of the rotor shaft.

Disclosure of Invention

The invention discloses a cooling design of a pump rotor aiming at the problems in the prior art, which is used for solving the following technical problems:

the invention aims to provide a cooling design of a pump rotor, which is used for solving the problem of heat conduction after a rotating rotor does work, cooling the rotating rotor and reducing the heat conducted along a rotor shaft, so that the risk of interference of meshed rotors due to thermal expansion is reduced, the temperature of a bearing and a sealing part is reduced, particularly for a lip seal, the friction heat between a lip and a shaft sleeve can be effectively reduced, the performance life of the lip seal is greatly prolonged, the frequency of replacing or adding bearing lubricating oil is reduced, and the reliability is improved.

In order to achieve the purpose, the invention is realized by the following technical scheme:

a cooling design of a pump rotor is characterized in that one or two equidistant spiral spring-like components, a base capable of fixing the spring-like components, a shaft sleeve and a thin-wall pipe are arranged in the rotor, the shaft sleeve is fastened through a lock nut or other axial pressure applying modes, or the thin-wall pipe is fixed only through a fixing bolt on the shaft sleeve, holes formed in the shaft sleeve are respectively arranged at two sealed space positions, a cooling medium can be filled in the sealed hole position space at the outer side, and the cooling medium can be liquid or gas, or the sealed hole position space at the inner side is filled with the cooling medium. When the rotor rotates, the pumping effect is realized by the spring-like component, and under the lead angle guide and lead angle thrust of the spring-like component, a medium for cooling enters the rotor, and along with the pressure and centrifugal action of the pumping effect, liquid or gas after heat exchange is thrown out through the opening on the shaft sleeve and is discharged through the reserved channel, so that the process of cooling the rotating rotor is completed.

It should be understood by those skilled in the relevant art that, in designing the rotor and rotor shaft as separate bodies, in order for the interface between the shaft and the rotor to be able to carry sufficient torque, the engagement surfaces must have a sufficient width (length) that for those rotor shapes having a large width (length), the width (length) of the engagement surfaces that carry torque and remain with sufficient margin, still occupies only a small portion of the entire rotor width (length) dimension, however, for the rotor shaft, the torque is only a necessary part, especially for the rotors needing to work together with the meshed rotors, the rigidity of the rotor shaft is a necessary condition for ensuring the stability of the clearance between the meshed rotors, such as screw vacuum pumps or compressor rotors, roots vacuum pumps or blower rotors, claw vacuum pumps or compressors, etc.

Due to the rigidity requirement, the first critical rotating speed of the rotor shaft is an important technical index for measuring the running stability of the rotor shaft. Those skilled in the art of machinery will appreciate that this criterion is one of the most important criteria for the design of a stepped shaft structure.

Before seeking to transfer heat through the rotor, torque and critical speed are the most important components that must be measured, the rotating rotor is made concentric with the shaft bore by further enlarging the inner diameter of the inner bore by the remaining rotor width (length) while maintaining a sufficient torque-satisfying combined surface area and shaft design, strength below the first critical speed, and the inner diameter is made larger than the shaft diameter through this point, and the following components can be installed within this difference in inner diameter and shaft diameter radii: one or two equidistant spiral spring-like components, a base which can fix the spring-like components, a shaft sleeve and a thin-wall pipe. The spring-like component can cling to the shaft by means of the mechanical property of the material of the spring-like component, the outer diameters of the thin-wall pipe and the spring-like component form a matched size and are fixed through the fixing base, and a cavity channel can be formed among the thin-wall pipe, the inner and outer apertures of the rotor and the inner diameter of the shaft sleeve. The sleeve is tightened by means of a lock nut or other means of applying axial pressure, or is only secured by means of a fixing bolt on the sleeve.

The linear diameter of the spring-like component is required to be more than or equal to 1mm, and the inner diameter of the spring-like component is required to be less than or equal to the shaft diameter of the installation position, so that the spring-like component can be tightly attached to the shaft by means of the mechanical property of the material of the spring-like component, preferably, the installation direction of the spring-like component meets the condition that the lead angle of the spiral of the spring-like component along with the rotation of the rotor is increased towards the inner part of the rotor. The two ends of the spring-like component are respectively provided with a convex design which is vertical to the radial direction so as to be convenient for fixing. It will be well understood by those skilled in the relevant art that the spring-like member may have a plurality of raised designs at each end.

The base of the fixed spring component is provided with a hole (groove) which can be used for fixing the convex part on the end surface of the spring component, a ladder which is used for fixing the thin-wall pipe and a width surface which is connected with the shaft.

The sleeve has 2 or more openings near the axial ends, preferably 2 openings, and each opening has one side located on a center line when viewed in a radial section, the other side perpendicular to the center line, one opening in a forward direction and one opening in a reverse direction. Preferably, the positions of the two openings are radially distributed at positions which satisfy the balance of radial forces and are axially spaced by more than or equal to 5mm, in order to leave a position in which a shaft seal can be mounted. Depending on the direction of rotation of the shaft, it is preferred that the opening direction is reversed in the direction closer to the rotor, and the opening direction is forward in the outer direction. Preferably, the open channel area of the outer side is greater than or equal to the open area of the inner side. A step is reserved at the position, close to the rotor direction, of the shaft sleeve and is used for being matched and connected with the end face of the rotor and the outer hole diameter of the rotor and reserving a groove of an O-shaped ring, and a gasket can be selected for sealing or is designed into a flange shape to fix the step through bolts. The inner diameter of the shaft sleeve is larger than the outer diameter of the thin-walled tube, and preferably, the diameter difference is larger than or equal to 2 mm. A step is designed between two opening positions on the shaft sleeve and used for fixing the thin-walled tube, the inner diameter of the outermost opening in the direction close to the axial tail end is designed to be matched with the shaft, and a certain width dimension is reserved for bearing radial stress and a small amount of torque of a part of the shaft. Those skilled in the relevant art will appreciate that the sleeve may be formed from two segments that are joined by interference or clearance, or welded.

The wall thickness of the thin-wall pipe needs to be more than or equal to 0.5mm, the inner diameter of the thin-wall pipe is equal to the sum of the shaft diameter of the installation position and the linear diameter of the spring-like component which is 2 times of the shaft diameter, and the inner diameter of the thin-wall pipe can form a matched size with the outer diameter of the spring-like component. The end part installed in the rotor is provided with an opening at a slight distance from the fixed base, and the number of the openings can be multiple, but the force applied to the end part for keeping the thin-wall pipe fixed needs to be considered. The outer diameter of the thin-wall pipe is required to be smaller than the inner and outer apertures of the rotor and the inner diameter of the shaft sleeve, and the diameter difference is larger than or equal to 2mm, so that a cavity channel can be formed among the thin-wall pipe, the inner and outer apertures of the rotor and the inner diameter of the shaft sleeve.

The sleeve is tightened by means of a lock nut or other means of applying axial pressure, or is only secured by means of a fixing bolt on the sleeve. Thus, when the two bores formed in the sleeve are respectively disposed at two sealed space positions according to the above design method, and the sealed outer bore position space is filled with a cooling medium, it should be understood by those skilled in the relevant art that the cooling medium may be liquid or gas, or the sealed inner bore position space is filled with a cooling medium, depending on the helix angle direction of the spring-like member when the spring-like member is installed. When the rotor rotates, the pumping effect is realized by the spring-like component in the thin-wall pipe, and under the lead angle guide and lead angle thrust of the spring-like component, a medium for cooling can enter the rotor, and under the pressure of the pumping effect caused by the difference of the linear speed in the thin-wall pipe and the linear speed of the inner and outer apertures of the rotor and the lead angle from the spiral, the cooling medium is introduced into the cavity between the inner and outer apertures of the rotor and the thin-wall pipe through the thin-wall pipe for heat exchange. And along with the pressure of pumping effect and the condition of different density of cooling medium after heat exchange and centrifugal action, the medium after heat exchange is thrown out through the opening on the inner side of the shaft sleeve and is discharged through a channel reserved at the position of the sealed opening serving as an outlet, so that the process of cooling the rotating rotor is completed, the temperature of the rotor and the heat transferred in the axial direction are reduced, when the lip seal is used as main seal, the friction heat between the lip and the shaft sleeve can be taken away at any time, the temperature rise is controlled to a lower degree, and the reliability and the service life of the lip seal are greatly prolonged.

It is well understood by those skilled in the relevant art that all the shapes of the openings on the thin-walled tube and the sleeve can be arbitrary when the cooling medium with a certain pressure is introduced from the outside, and the above-mentioned opening description and the process of throwing out the cooling medium are only a preferable way, although the cooling medium with a certain pressure will have a larger flow speed under the pressure and the spiral angle of the spring-like component will have a larger flow speed to complete the process of heat conduction of the rotor through the cavity channel, however, this will additionally increase the resistance and the stirring power loss, thereby additionally increasing the power loss of the pump.

Those skilled in the relevant arts will fully understand that the spring-like member may be mounted in a direction along with the rotation of the rotor, the lead angle of the spiral may be increased from the inside of the rotor to the end, and the spring-like member may be mounted between the shaft sleeve and the thin-walled tube to achieve the purpose of the present invention, and two spring-like members may be respectively disposed between the shaft sleeve and the thin-walled tube and between the inner and outer apertures of the rotor and the thin-walled tube to achieve the purpose of the present invention.

Preferably, the cooling medium is a lubricant for mounting the rotating rotor apparatus, and it is well understood by those skilled in the relevant art that the cooling medium may also be a gas.

A spring-like element is only one preferred way to achieve the pumping effect economically, which can still be achieved by machining equidistant helical grooves on the shaft or on the sleeve or both instead of a spring-like element.

The rotary rotor can be a rotor for a screw vacuum pump or a compressor, a rotor for a roots vacuum pump or a blower, a rotor for a claw vacuum pump or a compressor, a rotor for a scroll vacuum pump or a compressor, a rotor for a turbine, or other rotors which utilize centrifugal action generated by rotation to do work.

Compared with the prior art, the invention has the following advantages:

1. compared with the pump rotor cooling method in the prior art, the pump rotor cooling design can achieve the purpose of cooling the rotor through cooling medium circulation more effectively, and meanwhile can be achieved economically.

2. Compared with the pump rotor cooling method in the prior art, the pump rotor cooling design can realize pump rotor cooling under the condition of not reducing the strength of the rotor and the shaft. And the friction temperature rise of the lip mouth of the lip seal can be reduced when the lip seal is used as main seal, so that the reliability and the service life of the lip seal are greatly prolonged.

Description of the drawings:

FIG. 1 is a schematic view showing a cooling structure of a pump rotor according to embodiment 1 of the present invention;

FIG. 2 shows a complete structural schematic of a rotor cooling design of embodiment 1;

FIG. 3 is a schematic view showing a cooling structure of a pump rotor according to embodiment 2 of the present invention;

FIG. 4 shows a complete structural schematic of a rotor cooling design of embodiment 2;

FIG. 5 illustrates a front view, a side view and a cross-sectional view of an embodiment bushing;

FIG. 6 shows front and side views of an embodiment thin walled tube;

FIG. 7 illustrates front and side views of an embodiment spring-like member;

FIG. 8 shows front and side views of the mounting base of the thin walled tube and spring-like member of example 2.

The specific implementation mode is as follows:

preferred features of the present invention will be described in detail below by way of example with reference to the accompanying drawings, it being understood that the drawings described below are illustrative of only some embodiments of the invention, and that other embodiments may be devised by those skilled in the relevant art based on the principles of the description and these drawings without the use of inventive faculty.

Example one

As shown in fig. 1, the cooling design of a pump rotor of the present invention comprises a shaft sleeve 11, a fixed base 12, a thin-walled tube 13, and a spring-like member 14, which are installed in the space between a shaft 3 and a rotor 1, so as to form a cavity channel 131 between the rotor 1 and the thin-walled tube 13, and fix the shaft sleeve by a lock nut 31, wherein the rotor 1 can be a rotor for a screw vacuum pump or a compressor, a roots vacuum pump or a blower, a claw vacuum pump or a compressor, a scroll vacuum pump or a compressor, a turbine, or other rotors which use centrifugal action generated by rotation to do work, the shaft 3 retains a contact surface 32 with a sufficient width to be connected with the rotor 1, so that the joint surface area and the strength of the shaft 3 can satisfy the torque and meet the requirement of being lower than a first critical rotation speed, and supports the radial load and a small amount of torque of the shaft 3 portion through the contact surface 115 retained by the sleeve 11.

The shaft sleeve 11 is provided with a first opening 111 for discharging a cooling medium, a second opening 112 for filling the cooling medium, a fixing hole 116 for fixing the spring-like component 14, a step 114 for fixing the thin-wall pipe 13, the thin-wall pipe 13 is provided with an opening 132 for discharging the cooling medium, and a cavity channel 131 is formed by the thin-wall pipe 13 and the inner and outer apertures of the rotor 1 and the shaft sleeve 11. The first opening 111 and the second opening 112 are formed in the sleeve 11 in the direction close to the axial ends, and the number of the openings may be plural. The openings 132 in the thin-walled tube 13 can also be provided in a plurality, which are sealed off from the cooling medium entering the pump chamber by mounting a static seal 151 on the positioning flange 16 of the shaft sleeve 11, and likewise, for the cooling medium entering the rotor in the axial direction, a static seal 310 is fixed in the rotor by means of the fixing base 12. It will be appreciated by those skilled in the art that the spring-like member 14 may be mounted outside the thin-walled tube or may be mounted in both locations.

It is well understood by those skilled in the relevant art that all shapes of the openings on the thin-walled tube and the sleeve can be arbitrary when the cooling medium entering from the outside has a certain pressure, and the openings in claims 1, 4 and 5 describe and the process of throwing out the cooling medium is only a preferable way, although the cooling medium with a certain pressure will have a larger flow speed and flow rate under the action of the pressure and the spiral angle of the spring-like member 14 will complete the process of heat conduction of the rotor 1 through the cavity channel 131, however, this will additionally increase the resistance and the stirring power loss, thereby additionally increasing the power loss of the pump.

As shown in fig. 2, by placing the first and

second openings

111 and 112 in the sleeve into the component 2 where the first, second and

third seals

41, 42 and 43 are installed, there may be more or less seals, so that the opening 111 in the sleeve is located between the first and

second seals

41 and 42, forming a sealed space 232, and leaving the second passage 22 in the sealed space. The second opening 112 of the sleeve is located between the second seal 42 and the third seal 43, forming a sealed space 231, and leaving the first passage 21 in this sealed space.

The cooling medium enters the sealed space 231 through the first channel 21 on the component 2, and when the rotor 1 rotates, the cooling medium can introduce the cooling medium into the rotor along with the helix angle of the spring-like component 14 through the formed pumping effect, and enters the cavity channel 131 through the thin-wall pipe opening 132 for heat exchange, and then under the pressure of the pumping effect and the centrifugal action, the cooling medium after heat exchange is "thrown" out through the opening 111 on the shaft sleeve and then discharged through the channel 22, so that the cooling process of the pump rotor is completed. It will be understood by those skilled in the relevant art that the openings of the second passage 22 and the first passage 21 may be designed such that either passage is an inlet or an outlet, depending primarily on the direction of the helix angle of the spring-like member and whether the spring-like member is mounted inside or outside the thin-walled tube.

As shown in fig. 6, the thin walled tube 13 has an opening 132.

As shown in fig. 7, the spring-like member 14 has a first protrusion 141 and a second protrusion 143 at two ends thereof for fixing, respectively, and has a wire diameter 142.

As shown in fig. 8, the fixing base 12 has a hole (groove) 122 for fixing the end face protrusion of the spring-like member 14, a joint face 123 for connecting with a shaft, and a step 121 for fixing the thin-walled tube.

Example two

As shown in fig. 3, the cooling design of a pump rotor of the present invention comprises a shaft sleeve 11, a fixed base 12, a thin-walled tube 13, and a spring-like member 14, which are installed in the space between the shaft 3 and the rotor 1, so as to form a cavity channel 131 between the rotor 1 and the thin-walled tube 13, and fix the shaft sleeve by bolts through a fixing hole 113 at a flange 16 on the shaft sleeve 11, wherein the rotor 1 can be a rotor for a screw vacuum pump or a compressor, a roots vacuum pump or a blower, a claw vacuum pump or a compressor, a scroll vacuum pump or a compressor, a turbine, or other rotors for doing work by centrifugal action generated by rotation, the shaft 3 has a contact surface 32 with a sufficient width to be connected with the rotor 1, so that the shaft 3 can have a joint surface area satisfying torque and a strength below a first critical rotation speed, and supports the radial load and a small amount of torque of the shaft 3 portion through the contact surface 115 retained by the sleeve 11.

The shaft sleeve 11 is provided with a first opening 111 for discharging a cooling medium and a second opening 112 for filling the cooling medium, the thin-wall pipe 13 is provided with an opening 132 for discharging the cooling medium, a cavity channel 131 is formed by the thin-wall pipe 13, the inner and outer apertures of the rotor 1 and the shaft sleeve 11, and the shaft sleeve 11 can be provided with a plurality of the first openings 111 and the second openings 112 in the direction close to the axial tail end. The openings 132 in the thin-walled tube 13 can also be provided in a plurality, which are sealed off from the cooling medium entering the pump chamber by mounting a static seal 151 on the positioning flange 16 of the shaft sleeve 11, and likewise, for the cooling medium entering the rotor in the axial direction, a static seal 310 is fixed in the rotor by means of the fixing base 12. It will be appreciated by those skilled in the art that the spring-like member 14 may be mounted outside the thin-walled tube or may be mounted in both locations.

As shown in fig. 4, by placing the first opening 111 and the second opening 112 in the shaft sleeve into the component 2 where the first seal 41, the second seal 42 and the third seal 43 are installed, there may be more or less seals, so that the first opening 111 in the shaft sleeve is located between the first seal 41 and the second seal 42, a sealed space 232 is formed, and the second passage 22 is left in the sealed space. The second opening 112 of the sleeve is located between the second seal 42 and the third seal 43, forming a sealed space 231, and leaving the first passage 21 in this sealed space.

As shown in fig. 5, the sleeve 11 has a positioning flange 16, a fixing hole 113 on the flange 16, a step 114 for fixing the thin-walled tube, a hole (groove) 116 for fixing a protruding portion on the end face of the spring-like member 14, a contact surface 115 for bearing a part of the radial load of the shaft 3, a second opening 112 for allowing a cooling medium to enter, and a first opening 111 for discharging the cooling medium.

As shown in fig. 6, the thin walled tube 13 has an opening 132.

As shown in fig. 7, the spring-like member 14 has a first protrusion 141 and a second protrusion 143 at two ends for fixing, and there may be more protrusions with a wire diameter 142.

As shown in fig. 8, the fixing base 12 has a hole (groove) 122 for fixing the end face protrusion of the spring-like member 14, a joint face 123 for connecting with a shaft, and a step 121 for fixing the thin-walled tube 13.

Claims

1. A cooling design of a pump rotor is characterized in that one or two equidistant spiral spring-like components, a base capable of fixing the spring-like components, a shaft sleeve and a thin-walled tube are arranged in the rotor, the shaft sleeve is fastened through a lock nut or other axial pressure applying modes, or the thin-walled tube is fixed only through a fixing bolt on the shaft sleeve, holes formed in the shaft sleeve are respectively arranged at two sealed space positions, a cooling medium can be filled in the hole position space at the sealed outer side, and the cooling medium can be liquid or gas, or the hole position space at the sealed inner side is filled with the cooling medium; when the rotor rotates, the pumping effect is realized by the spring-like component, and under the lead angle guide and lead angle thrust of the spring-like component, a medium for cooling enters the rotor, and along with the pressure and centrifugal action of the pumping effect, liquid or gas after heat exchange is thrown out through the opening on the shaft sleeve and is discharged through the reserved channel, so that the process of cooling the rotating rotor is completed.

2. A cooling arrangement for a pump rotor according to claim 1, wherein the spring-like element has one or more projections at each end, preferably one projection at each end, to facilitate fastening.

3. A cooling design of a pump rotor according to claim 1, characterized in that the base of the fixed spring-like component is provided with a hole (groove) for fixing the raised part on the end face of the spring-like component and a step for fixing the thin-walled tube.

4. A cooling design of pump rotor as claimed in claim 1, wherein the sleeve is formed by two sections of interference or clearance joint or welded, and has 2 or more openings near the axial ends; preferably, there are 2 openings, and each opening has one side located on a central line when viewed in a radial section, and the other side perpendicular to the central line, one being a forward opening and the other being a reverse opening; preferably, the positions of the two openings are distributed radially in positions that satisfy the balance of radial forces and that keep them axially apart from each other in a position in which a shaft seal can be mounted; a step is designed between two opening positions on the shaft sleeve and used for fixing the thin-walled tube, the inner diameter of the outermost opening in the direction close to the axial tail end is designed to be matched with the shaft, and a certain width dimension is reserved for bearing radial stress and a small amount of torque of a part of the shaft.

5. A cooling design of pump rotor according to claim 1, characterized in that the end of the thin-walled tube installed into the rotor has an opening at a slight distance from the fixed base, and the opening can be multiple.

6. A cooling design of pump rotor according to claim 1, characterized in that the shaft sleeve is fastened by locking nut or other means of applying axial pressure, or only fixed by fixing bolt on the shaft sleeve.

7. A cooling design of pump rotor as claimed in claim 1, characterized by that the pumping effect is achieved by machining equidistant helical grooves on the shaft or on the sleeve or both instead of spring-like parts.

8. A cooling arrangement for a pump rotor as claimed in claim 1, wherein the rotor is of the type used in a screw vacuum pump or compressor, a roots vacuum pump or blower, a claw vacuum pump or compressor, a scroll vacuum pump or compressor, a turbine or other rotor which uses centrifugal action generated by rotation to produce work.