CN220769733U

CN220769733U - Centrifugal compression device

Info

Publication number: CN220769733U
Application number: CN202322188637.5U
Authority: CN
Inventors: 王琼; 张志军; 辛志铎
Original assignee: Xunshi Technology Suzhou Co ltd
Current assignee: Xunshi Technology Suzhou Co ltd
Priority date: 2023-08-15
Filing date: 2023-08-15
Publication date: 2024-04-12
Anticipated expiration: 2033-08-15

Abstract

The utility model discloses a centrifugal compression device, which comprises a hollow first rotating body which is horizontally arranged, one end of the first rotating body is connected with a second rotating body, the second rotating body is movably and fixedly arranged at the center of an impeller, the impeller is movably embedded in a volute, one side of the impeller, which faces the first rotating body, is provided with an air inlet, the end part of the first rotating body, which is far away from the second rotating body, is provided with a thrust bearing disc, the first rotating body is also sleeved with a gas bearing and a thrust bearing, a branch channel penetrating the first rotating body is arranged in the first rotating body, and a thrust cooling channel is formed in the thrust bearing disc along the circumferential direction.

Description

Centrifugal compression device

Technical Field

The utility model belongs to the technical field of centrifugal compression devices, and particularly relates to a centrifugal compression device.

Background

Centrifugal compression devices are devices that draw fluid in the direction of a rotating embedded shaft and eject it in the circumferential direction, thereby compressing and pumping the fluid.

The existing centrifugal compression device has the problems that the thrust bearing disc rotates along with the rotation of the rotating shaft, and the contact friction between the thrust bearing disc and the concave-convex part of the top foil of the thrust bearing causes air gap damage and temperature rise, and causes heating, abrasion, power loss and the like; and when the temperature rises rapidly, the bearing performance decreases; further, the high-temperature gas compressed by the impeller reduces the durability of the centrifugal compressor. There is a need for a solution to the above-mentioned problems.

The foregoing is not necessarily a prior art, and falls within the technical scope of the inventors.

Disclosure of Invention

In order to solve the above problems, an object of the present utility model is to provide a centrifugal compressor device capable of cooling a rotating body and a thrust bearing disk while rotating, and improving cooling efficiency.

In order to achieve the above object, the present utility model provides a centrifugal compression device, which comprises a first hollow rotating body arranged horizontally, wherein one end of the first rotating body is connected with a second rotating body, the second rotating body is movably fixed at the center of an impeller, the impeller is movably embedded in a volute, an air inlet is formed at one side of the impeller, which faces the first rotating body, an end part of the first rotating body, which is far away from the second rotating body, is provided with a thrust bearing disc, a gas bearing and a thrust bearing are further sleeved on the first rotating body, the thrust bearing is abutted against one side of the thrust bearing disc, which is close to the second rotating body, a branch channel penetrating through the first rotating body is formed in the first rotating body, the gas bearing is positioned at one side of the branch channel, which is far away from the second rotating body, and a thrust cooling channel is formed in the thrust bearing disc along the circumferential direction.

In one example, the first rotating body, the second rotating body, and the thrust bearing disc are integrally formed.

In one example, a diffuser is disposed within the volute, the diffuser in communication with the impeller.

In one example, the branch passage is formed through an outer peripheral surface of the first rotating body so as to intersect with an axial direction of the gas bearing, the branch passage being located on a side of the gas bearing close to the second rotating body.

In one example, a central cooling passage penetrating the tip end of the first rotating body and communicating with the penetrating portion of the gas bearing provided in the circumferential direction is provided in the axial direction of the first rotating body, and the branch passage and the thrust cooling passage are both in communication with the central cooling passage.

In one example, a plurality of the thrust cooling passages can be provided in the thrust bearing plate.

In one example, the diameter of the thrust cooling passage is less than the diameter of the central cooling passage.

In one example, the thrust cooling channels penetrate the first rotating body in a radial structure, and the thrust cooling channels are provided in an even-numbered structure.

In one example, a plurality of the branch passages can be provided in the first rotating body.

In one example, the branch passages penetrate the first rotating body in a radial structure, and the branch passages are provided in an even-numbered structure.

The centrifugal compression device provided by the utility model has the following beneficial effects:

1. the refrigerant flowing in through the thrust cooling channel cools the gas bearing while the rotating body rotates, so that the temperature rise is restrained, the damage of the top foil caused by the rotating friction of the gas bearing is prevented, and the effect of obviously improving the supporting performance of the gas bearing is achieved;

2. the thrust bearing can stably absorb the force acting on the axial direction of the impeller while improving the supporting performance of the gas bearing, so that defrosting can be effectively removed by controlling the thrust of the thrust bearing;

3. a central cooling passage formed in an axial direction of the rotating body and a branch passage branching from the central cooling passage to a radial bearing side, thereby cooling at a site close to the gas bearing, so that a rotation support performance of the gas bearing can be further improved;

4. the discharge space through the central cooling channel and the thrust cooling channel is communicated with the suction inlet of the impeller, so that the fluid discharged through the cooling channel is sucked to the impeller side, the fluid for cooling flows smoothly, the high-temperature fluid can be rapidly discharged to the outside, the viscosity increase of the gas around the gas bearing is restrained, and the rotation supporting performance can be remarkably improved.

Drawings

The accompanying drawings, which are included to provide a further understanding of the utility model and are incorporated in and constitute a part of this specification, illustrate embodiments of the utility model and together with the description serve to explain the utility model and do not constitute a limitation on the utility model. In the drawings:

fig. 1 is a schematic cross-sectional side view of a first rotor of a centrifugal compressor according to the present utility model.

Fig. 2 is a schematic side sectional view of a centrifugal compressor of the present utility model.

Fig. 3 is a schematic view of the thrust cooling channel and the branch channel according to the present utility model.

Fig. 4 is a schematic view of a thrust cooling channel and a branching channel according to the present utility model.

Fig. 5 is a schematic view of another structure of the thrust cooling channel and the branch channel of the present utility model.

Detailed Description

In order to more clearly illustrate the general inventive concept, a detailed description is given below by way of example with reference to the accompanying drawings.

In the description of the present utility model, it should be understood that the terms "center," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "axial," "radial," "circumferential," and the like indicate orientations or positional relationships based on the orientation or positional relationships shown in the drawings, merely to facilitate describing the present utility model and simplify the description, and do not indicate or imply that the devices or elements referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present utility model.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include one or more such feature. In the description of the present utility model, the meaning of "a plurality" is two or more, unless explicitly defined otherwise.

In the present utility model, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; the device can be mechanically connected, electrically connected and communicated; can be directly connected or indirectly connected through an intermediate medium, and can be communicated with the inside of two elements or the interaction relationship of the two elements. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.

In the present utility model, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. In the description of the present specification, the description with reference to the terms "one aspect," "some aspects," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the aspect or example is included in at least one aspect or example of the present utility model. In this specification, the schematic representations of the above terms are not necessarily for the same scheme or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more aspects or examples.

As shown in fig. 1 to 5, the embodiment of the present utility model proposes a centrifugal compressor, which is characterized by comprising a hollow first rotor 1 horizontally arranged, one end of the first rotor 1 is connected with a second rotor 2, the second rotor 2 is movably and fixedly arranged at the center of an impeller 3 to drive the impeller 3 to rotate, the impeller 3 is movably embedded in a volute 4, one side of the impeller 3 facing the first rotor 1 is provided with an air inlet 5, the impeller 3 connected with one end of the first rotor 1 rotates together with the first rotor 1 due to the high-speed rotation of the first rotor 1, the impeller 3 sucks fluid into the axial direction through the air inlet 5 and discharges the fluid in the radial direction, and the fluid is sucked into the air inlet 5 through the air outlet of the volute 4 and is discharged by centrifugal force, so that the centrifugal compressor can continuously execute the compression and suction action of the fluid, the end of the first rotor 1 far away from the second rotor 2 is provided with a thrust bearing disk 6, the first rotor 1, the second rotor 2 and the thrust bearing disk 6 are integrally formed, the first rotor 1 is also sleeved with a gas bearing 7 and a thrust bearing 8, the thrust rotor 8 is abutted against the first rotor 1 and the thrust bearing 8 is formed in a cooling channel 11, the cooling channel is formed on one side of the first rotor 1, the cooling channel is formed by the first rotor 1, the cooling channel is separated from the first rotor channel 11, the cooling channel is formed by the first rotor channel is separated from the first rotor channel 11, the first channel is cooled by the thrust channel 11, and the cooling channel is cooled down by the air channel is separated from the first channel, and the first channel is cooled down by the air channel, the air channel is cooled down by the air channel, and the air is cooled down through the air channel, and the air channel is cooled down through the air channel, and the air is cooled through, and the air and cooled through, and, to prevent an increase in viscosity due to an increase in temperature of surrounding gas disposed in a gas bearing 7 of a centrifugal compressor.

Specifically, a diffuser 9 is arranged in the volute 4, the diffuser 9 is communicated with the impeller 3, liquid is collected by the impeller 3 and is accelerated to be thrown into the diffuser 9, and finally pumped out from the discharge port of the volute 4.

Specifically, the branch passage 11 is formed so as to intersect the axial direction of the gas bearing 7 to penetrate the branch passage 11 of the outer peripheral surface of the first rotary body 1, the branch passage 11 is located on the side of the gas bearing 7 close to the second rotary body 2, the gas bearing 7 is a non-contact bearing, and the gas bearing 7 is used to minimize friction generated by the rotation of the first rotary body 1, since the non-direct contact with the first rotary body 1 using gas as a lubricating medium is achieved.

Specifically, a central cooling passage 12 that penetrates the tip of the first rotating body 1 and communicates with the penetration portion of the gas bearing 7 disposed in the circumferential direction is opened in the axial direction of the first rotating body 1, and both the branch passage 11 and the thrust cooling passage 61 communicate with the central cooling passage 12.

Specifically, a plurality of thrust cooling passages 61 can be provided in the thrust bearing 8 disk 6.

Specifically, the diameter of the thrust cooling passage 61 is smaller than the diameter of the center cooling passage 12.

Specifically, the thrust cooling passages 61 penetrate the first rotating body 1 in a radial configuration, and the thrust cooling passages 61 are provided in an even number configuration, which may be a 2-passage configuration, a 4-passage configuration, or a 6-passage configuration and even number of configurations above.

Specifically, the first rotating body 1 can be provided with a plurality of branch passages 11.

Specifically, the branch passages 11 penetrate the first rotating body 1 in a radial structure, and the branch passages 11 are provided in an even number structure, which may be a 2-passage structure, a 4-passage structure, or a 6-passage structure and even number structures above.

Working principle: the centrifugal compressor is characterized in that the centrifugal compressor is formed by rotating the first rotating body at a high speed, rotating the impeller connected with one end of the first rotating body together, sucking fluid in the axial direction through the air inlet, and discharging the fluid in the radial direction, wherein the fluid sucked through the air inlet is pressurized and discharged through the discharge port of the volute by centrifugal force along with the rotation of the impeller, so that the centrifugal compressor can continuously execute compression and suction work of the fluid; in this process, the central cooling passage, the branch passages and the external refrigerant air flowing in through the thrust cooling passage realize a magnetic force type cooling effect to prevent an increase in viscosity due to a temperature rise of the gas around the gas bearing disposed in the centrifugal compressor; oil-free gas bearing for oil film and lubrication film by gas to minimize friction force generated by rotation of first rotating body

The fluid outside the centrifugal compression device is introduced into the penetrating portion of the end portion of the first rotating body through the air gap formed through the thrust bearing, so that the inflowing fluid effectively cools the gas bearing and the surrounding gas by achieving a cooling effect and a heat conduction effect on the centrifugal compression device.

A part of the fluid flowing in flows into the inner side of the thrust bearing disk through the central cooling passage, cools the thrust bearing disk, and then is discharged to the outside along the thrust cooling passage penetrating the thrust bearing.

The other part of the fluid is branched to the end side of the gas bearing provided at both ends of the rotor by the central cooling passage, and moves to the outside of the penetrating first rotor and the penetrating branch passage, respectively, and the first rotor is effectively cooled by the plurality of branch passages, and the air gap of the gas bearing is also affected, whereby the inside of the centrifugal compressor can be cooled more effectively.

In this specification, each embodiment is described in a progressive manner, and identical and similar parts of each embodiment are all referred to each other, and each embodiment mainly describes differences from other embodiments. In particular, for system embodiments, since they are substantially similar to method embodiments, the description is relatively simple, as relevant to see a section of the description of method embodiments.

The foregoing is merely exemplary of the present utility model and is not intended to limit the present utility model. Various modifications and variations of the present utility model will be apparent to those skilled in the art. Any modification, equivalent replacement, improvement, etc. which come within the spirit and principles of the utility model are to be included in the scope of the claims of the present utility model.

Claims

1. The utility model provides a centrifugal compression device, its characterized in that includes the hollow first rotator of level setting, second rotator is connected to first rotator one end, the second rotator activity sets firmly in the centre of a circle department of impeller, the impeller activity inlays and establishes in the spiral case, the impeller is towards one side of first rotator has seted up the air inlet, the tip that first rotator kept away from the second rotator is provided with thrust bearing dish, still the cover is equipped with gas bearing and thrust bearing on the first rotator, thrust bearing is in close to one side that the thrust bearing dish is close to the second rotator, set up in the first rotator and run through the branch passageway of first rotator, gas bearing is located the branch passageway is kept away from one side of second rotator the inside of thrust bearing dish is formed with thrust cooling channel along the circumferencial direction.

2. The centrifugal compressor apparatus of claim 1, wherein the first rotary body, the second rotary body, and the thrust bearing disk are integrally formed.

3. A centrifugal compressor according to claim 1, wherein a diffuser is disposed within the volute, the diffuser being in communication with the impeller.

4. The centrifugal compressor according to claim 1, wherein the branch passage is formed through an outer peripheral surface of the first rotating body so as to intersect an axial direction of the gas bearing, the branch passage being located on a side of the gas bearing close to the second rotating body.

5. The centrifugal compressor according to claim 1, wherein a central cooling passage penetrating a distal end of the first rotating body and communicating with a penetrating portion of the gas bearing provided in a circumferential direction is provided in an axial direction of the first rotating body, and the branch passage and the thrust cooling passage are both communicated with the central cooling passage.

6. The centrifugal compressor apparatus of claim 5, wherein a plurality of said thrust cooling passages are provided in said thrust bearing plate.

7. The centrifugal compressor apparatus of claim 5, wherein the diameter of the thrust cooling passage is smaller than the diameter of the central cooling passage.

8. The centrifugal compressor according to claim 6, wherein said thrust cooling passages penetrate said first rotary body in a radial configuration, said thrust cooling passages being provided in an even configuration.

9. A centrifugal compressor according to claim 1, wherein a plurality of said branch passages are provided in said first rotating body.

10. A centrifugal compressor according to claim 9, wherein said branch passages penetrate said first rotary body in a radial configuration, said branch passages being provided in an even configuration.