CN112343816B

CN112343816B - Bidirectional floating pressing mechanism for reducing friction of moving turbine disc

Info

Publication number: CN112343816B
Application number: CN202011166144.6A
Authority: CN
Inventors: 钱永贵; 王飞
Original assignee: Nanjing Desheng Power Technology Co ltd
Current assignee: Nanjing Desheng Power Technology Co ltd
Priority date: 2020-10-27
Filing date: 2020-10-27
Publication date: 2022-07-26
Anticipated expiration: 2040-10-27
Also published as: CN112343816A

Abstract

The invention provides a bidirectional floating pressing mechanism for reducing friction of a moving turbine disc, which comprises a cylindrical main bearing seat, wherein one end of the main bearing seat is connected with a compression part, a pressing part and a floating assembly are arranged in the main bearing seat, a main rotating shaft is connected in the main bearing seat, a first high-pressure gas channel is formed in the inner wall of the main bearing seat, the compression part comprises the moving turbine disc, one end, far away from the main rotating shaft, of the moving turbine disc is coupled with a static turbine disc, a high-pressure exhaust port is formed in the central axis of the radial plane of the static turbine disc, a low-pressure air suction port is formed in the outer peripheral surface of the static turbine disc, a second high-pressure gas channel is fixed on the outer peripheral surface of the static turbine disc, the pressing part comprises a gap, and a floating block is slidably connected in the gap. The invention optimizes the problem that the efficiency of the compressor is influenced by the increase of the exhaust pressure of the compressor by the fact that the moving turbine disc is in a floating balance state under the action of left and right gas forces in the axial direction.

Description

Bidirectional floating pressing mechanism for reducing friction of moving turbine disc

Technical Field

The invention mainly relates to the technical field of compressors, in particular to a bidirectional floating pressing mechanism for reducing friction of a moving turbine disc.

Background

The scroll compressor is a compressible volume device consisting of a fixed involute turbine disk and an involute moving turbine disk which performs eccentric rotary translational motion.

According to Japanese patent floating compaction patent JPH0378586A, the slider of this product is one-way floating, and the hard contact between slider and the driving disk, frictional force are big, and its slider is whole ring, can either interfere in eccentric pin or balancing weight in the scroll compressor of eccentric pin structure, if avoid interfering, bypass eccentric pin and balancing weight, can cause the complete machine volume too big.

Disclosure of Invention

The invention mainly provides a bidirectional floating pressing mechanism for reducing friction of a moving turbine disc, which is used for solving the technical problems in the background technology.

The technical scheme adopted by the invention for solving the technical problems is as follows:

a bidirectional floating pressing mechanism for reducing friction of a movable turbine disc comprises a cylindrical main bearing seat, wherein one end of the main bearing seat is connected with a compression part, a pressing part and a floating assembly are arranged in the main bearing seat, the main bearing seat is connected with a main rotating shaft through a bearing, a first high-pressure gas channel is formed in the inner wall of the main bearing seat, the compression part comprises the movable turbine disc, the movable turbine disc is fixed at one end, away from the radial plane of the main bearing seat, of the main rotating shaft, the end, away from the main rotating shaft, of the movable turbine disc is coupled with a static turbine disc, the static turbine disc is fixed on a shell of the main bearing seat, a high-pressure gas exhaust port is formed in the axial line of the radial plane of the static turbine disc, a low-pressure gas suction port is formed in the outer peripheral surface of the static turbine disc, and a second high-pressure gas channel is fixed on the outer peripheral surface of the static turbine disc, one end, far away from the turbine disc, of the second high-pressure gas channel penetrates through the outer peripheral face of the main bearing seat and extends to the interior of the main bearing seat to be communicated with the first high-pressure gas channel, the pressing component comprises a gap formed between the inner wall of the main bearing seat and the movable turbine disc, a floating block is connected to the interior of the gap in a sliding mode, the gap divides the interior of the gap into a first gas cavity and a second gas cavity through the floating block, a fourth high-pressure gas channel is formed in a shell of the floating block, and two ends of the fourth high-pressure gas channel are respectively communicated with the first gas cavity and the second gas cavity.

Furthermore, the floating assembly comprises a floating block retainer, the floating block retainer is fixed at one end, close to the dynamic turbine disc, of the main rotating shaft, the floating block retainer is located between the gap and the inner wall of the main bearing seat, a third high-pressure gas channel is formed in a shell of the floating block retainer, and two ends of the third high-pressure gas channel are respectively communicated with the second high-pressure gas channel and the first gas cavity.

Furthermore, an anti-rotation column is fixed on the surface of one side, close to the first air cavity, of the floating block retainer, and the anti-rotation column is not overlapped with the central axis of the radial plane of the first air cavity.

Furthermore, a pin hole matched with the anti-rotation column body is formed in the shell of the floating block.

Furthermore, a ripple spring is arranged between the floating block retainer and the floating block, and the ripple spring is fixed on one side surface of the floating block retainer close to the floating block.

Furthermore, a balancing weight is fixed on one side of the floating block retainer, which is far away from the moving turbine disc.

Furthermore, the compression component is connected with a sealing assembly, the sealing assembly comprises a first O-shaped ring, a second O-shaped ring and a third O-shaped ring, the first O-shaped ring is embedded in the inner wall of one end, far away from the second air cavity, of the first air cavity, the second O-shaped ring is embedded in the outer peripheral surface of the slider, and the third O-shaped ring is embedded in the inner wall of one end, far away from the first air cavity, of the second air cavity.

Furthermore, one side of the third O-shaped ring, which is close to the second O-shaped ring, is abutted with a self-lubricating wear-resistant sealing strip, and the self-lubricating wear-resistant sealing strip is embedded into the inner wall of one end, away from the first air cavity, of the two air cavities.

Furthermore, a plurality of anti-rotation eccentric pins are fixed on the inner wall of the main bearing seat, and are arranged around the central axis of the radial plane of the main bearing seat one by one in an equidistant mode and are parallel to the central axis.

Furthermore, an electroplated layer is arranged on the outer surface of the floating block.

Compared with the prior art, the invention has the beneficial effects that:

the invention can solve the problems that the back pressure of a movable disc is gradually increased due to the increase of the exhaust pressure of the compressor, the movable disc is not attached to a static disc any more, end face leakage is caused, and the efficiency of the compressor is influenced, and specifically comprises the following steps: the dynamic turbine disk is in a floating balance state under the action of left and right gas forces in the axial direction, the right end face of the dynamic turbine disk is in a contact critical state with the static turbine disk, the friction force between the tooth top and the tooth bottom face of the right scroll is solved, the left side of the dynamic turbine disk is in a contact critical state with the floating block, the friction force on the left side of the dynamic turbine disk is solved, the energy consumption is reduced, and the efficiency is improved.

The uniform distribution type bidirectional floating design is adopted, the problems of space arrangement and friction power consumption of the floating blocks are solved, the axial stress of the movable disc is balanced, the left bearing and the right bearing of the anti-rotation eccentric pin are not required to provide support for axial force, the noise of the bearings is reduced, the service life of the bearings is prolonged, and the use cost of the bearings is reduced.

The invention will be explained in detail below with reference to the drawings and specific embodiments.

Drawings

FIG. 1 is a schematic view of the overall structure of the present invention;

FIG. 2 is an enlarged view of the structure of area A of the present invention;

FIG. 3 is an exploded view of the present invention;

FIG. 4 is a schematic view of an internal structure of a main bearing housing according to the present invention;

FIG. 5 is a schematic structural view of a moving turbine disk of the present invention;

FIG. 6 is a schematic view of the slider retainer of the present invention.

In the figure: 1. a main bearing housing; 11. a main rotating shaft; 12. a first high-pressure gas passage; 13. an anti-rotation eccentric pin; 2. a compression member; 21. a moving turbine disk; 22. a stationary turbine disk; 23. a low-pressure air suction port; 24. a high pressure exhaust port; 25. a second high pressure gas passage; 3. a pressing member; 31. a gap; 32. a fourth high pressure gas channel; 33. a first air cavity; 34. a second air cavity; 35. a slider; 351. a pin hole; 4. a floating assembly; 41. a slider holder; 42. a third high pressure gas passage; 43. an anti-rotation cylinder; 44. a wave spring; 5. a seal assembly; 51. a first O-ring; 52. a second O-ring; 53. a third O-ring; 54. self-lubricating wear-resistant sealing strips; 6. and a balancing weight.

Detailed Description

In order to facilitate an understanding of the invention, the invention will now be described more fully hereinafter with reference to the accompanying drawings, in which several embodiments of the invention are shown, but which may be embodied in different forms and not limited to the embodiments described herein, but which are provided so as to provide a more thorough and complete disclosure of the invention.

It will be understood that when an element is referred to as being "secured to" another element, it can be directly on the other element or intervening elements may be present, and when an element is referred to as being "connected" to another element, it can be directly connected to the other element or intervening elements may also be present, as the terms "vertical", "horizontal", "left", "right" and the like are used herein for descriptive purposes only.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs, and the use of such term knowledge in the specification of the invention is for the purpose of describing particular embodiments and is not intended to be limiting of the invention, and the use of the term "and/or" herein includes any and all combinations of one or more of the associated listed items.

In an embodiment, referring to fig. 1 to 6, a bidirectional floating pressing mechanism for reducing friction of a moving turbine disc includes a cylindrical main bearing seat 1, one end of the main bearing seat 1 is connected with a compression component 2, the main bearing seat 1 is internally provided with a pressing component 3 and a floating component 4, the main bearing seat 1 is internally connected with a main rotating shaft 11 through a bearing, the inner wall of the main bearing seat 1 is provided with a first high-pressure gas passage 12, the compression component 2 includes a moving turbine disc 21, the moving turbine disc 21 is fixed at one end of the main rotating shaft 11 away from a radial plane of the main bearing seat 1, one end of the moving turbine disc 21 away from the main rotating shaft 11 is coupled with a static turbine disc 22, the static turbine disc 22 is fixed on a housing of the main bearing seat 1, and a high-pressure exhaust port 24 is formed at a central axis of the radial plane of the static turbine disc 22, the outer peripheral surface of the static turbine disc 22 is provided with a low-pressure air suction port 23, the outer peripheral surface of the static turbine disc 22 is fixedly provided with a second high-pressure air passage 25, one end, far away from the movable turbine disc 21, of the second high-pressure air passage 25 penetrates through the outer peripheral surface of the main bearing seat 1 and extends into the main bearing seat 1 to be communicated with the first high-pressure air passage 12, the pressing component 3 comprises a gap 31 formed between the inner wall of the main bearing seat 1 and the movable turbine disc 21, a floating block 35 is slidably connected inside the gap 31, the gap 31 divides the inside of the gap 31 into a first air cavity 33 and a second air cavity 34 through the floating block 35, a fourth high-pressure air passage 32 is arranged on a shell of the floating block 35, and two ends of the second high-pressure air passage 32 are respectively communicated with the first air cavity 33 and the second air cavity 34.

Specifically, referring to fig. 1 and 2, a plurality of anti-rotation eccentric pins 13 are fixed on an inner wall of the main bearing seat 1, the plurality of anti-rotation eccentric pins 13 are arranged around a central axis of a radial plane of the main bearing seat 1 at equal intervals one by one and are parallel to the central axis, one end of each anti-rotation eccentric pin 13, which is far away from the main bearing seat 1, sequentially penetrates through the slider holder 41 and the moving turbine disc 21, and since two ends of the moving turbine disc 21 are in a floating balance state under the action of the sliders 35 and the gas force in the axial direction, the anti-rotation eccentric pins 13 can be effectively avoided by the design of the uniform distribution type slider, the arrangement of the compressing component 3 is realized on the premise of not increasing the overall size of the structural component, the structural component of the whole machine is smaller, the material and the space are saved, and the bearings on the left and right sides of the anti-rotation eccentric pins 13 are liberated, and by the design of the uniform distribution type bidirectional floating, the floating block space arrangement and friction power consumption are solved, the dynamic turbine disc 21 is balanced in axial stress, the left bearing and the right bearing of the anti-rotation eccentric pin 13 are not needed to provide support for axial force, the noise of the bearings is reduced, the service life of the bearings is prolonged, and the use cost of the bearings is reduced.

Specifically, please refer to fig. 1 and 3 again, a ripple spring 44 is disposed between the slider holder 41 and the slider 35, and the ripple spring 44 is fixed on a side surface of the slider holder 41 close to the slider 35, so that when the slider 35 shakes due to the influence of the gas in the first air chamber 33 and the second air chamber 34, the ripple spring 44 abuts against the slider 35, so as to absorb the shake of the slider 35 by the compression and rebound of the ripple spring 44, and ensure that the slider 35 is always in the working position range, so that the whole pressing member 3 is stable without shaking and tilting.

Specifically, referring to fig. 1 to 3 again, the outer surface of the floating block 35 is provided with an electroplated layer, so as to reduce the friction coefficient, and the friction coefficient and the power consumption are reduced by using the self-lubricating wear-resistant sealing strip 54 and the surface of the floating block 35 through anodic oxidation or electroplating or other treatments, or the floating block 35 is replaced by a self-lubricating wear-resistant material, so as to reduce the friction coefficient and the power consumption.

Specifically, please refer to fig. 1, 3, 4, and 5 again, the floating assembly 4 includes a floating block holder 41, the floating block holder 41 is fixed at one end of the main rotating shaft 11 close to the moving turbine disc 21, the floating block holder 41 is located between the gap 31 and the inner wall of the main bearing seat 1, a third high-pressure gas passage 42 is opened on a housing of the floating block holder 41, two ends of the third high-pressure gas passage 42 are respectively communicated with the second high-pressure gas passage 25 and the first gas cavity 33, the pressing component 3 is separated from the counterweight block 6, the main rotating shaft 11, and the anti-rotation eccentric pin by the floating block holder 41 and a "uniform distribution type floating block — gas cavity" structure 13 to prevent interference, so that the above elements are not in the same vertical space, and are not influenced by the rotation of the counterweight block 6. And can provide space for increasing the axial thrust by increasing the sectional area of the slider 35.

Specifically, please refer to fig. 1 to 4 again, a weight block 6 is fixed on one side of the slider holder 41 away from the moving turbine disc 21, so that the complete machine is in a dynamic balance state during movement.

Specifically, please refer to fig. 1 to 5 again, an anti-rotation cylinder 43 is fixed on a surface of one side of the slider holder 41 close to the first air cavity 33, the anti-rotation cylinder 43 is not overlapped with a central axis of a radial plane of the first air cavity 33, and a pin hole 351 engaged with the anti-rotation cylinder 43 is formed on a housing of the slider 35, so that the anti-rotation cylinder 43 and the first air cavity 33 are not in the same center, and the slider 35 can be prevented from rotating by being engaged with the pin hole of the slider 35, so that the slider is always kept stable.

Specifically, referring to fig. 2 and 3, the compression member 2 is connected to a sealing assembly 5, the sealing assembly 5 includes a first O-ring 51, a second O-ring 52 and a third O-ring 53, the first O-ring 51 is embedded in an inner wall of the first air cavity 33 at an end away from the second air cavity 34, such that the first O-ring 51 embedded in the inner wall of the first air cavity 33 reduces a gap between the inner wall and the slider holder 41, thereby ensuring airtightness between the slider holder 41 and the first air cavity 33, the second O-ring 52 is embedded in an outer circumferential surface of the slider 35, such that the second O-ring 52 embedded in the outer circumferential surface of the slider 35 reduces a gap between the outer circumferential surface and the first air cavity 33 and the second air cavity 34, thereby ensuring airtightness between the slider 35 and the first air cavity 33 and the second air cavity 34, and the third O-ring 53 is embedded in an inner wall of the second air cavity 34 at an end away from the first air cavity 33, since the second air cavity 34 is opened on the moving turbine disk 21, the gap between the moving turbine disk 21 and the slider 35 is reduced by the third O-ring 53 on the moving turbine disk.

Specifically, please refer to fig. 2 and 3 again, a self-lubricating weather strip 54 abuts against one side of the third O-ring 53 close to the second O-ring 52, the self-lubricating weather strip 54 is embedded into the inner wall of one end of the second air cavity 34 far away from the first air cavity 33, the self-lubricating weather strip 54 is designed to be circular, rather than strip-shaped, and is supported and compensated by the third O-ring 53, so that gas leakage can be effectively reduced, and friction and power consumption can be reduced by using the self-lubricating weather strip 54 containing a teflon material.

The specific operation mode of the invention is as follows:

when the pressing mechanism is used, firstly, a motor spindle is inserted into the main rotating shaft 11, then the motor is started to drive the main rotating shaft 11 to rotate, the main rotating shaft 11 drives the movable turbine disc 21 to move, gas is sucked from the low-pressure gas suction port 23, compressed and finally discharged from the high-pressure gas discharge port 24, the gas in the second high-pressure gas passage 25 is connected with the high-pressure gas discharge port 24, the gas passes through the second high-pressure gas passage 32 and the third high-pressure gas passage 42 under the action of the pressure and reaches the first gas cavity 33 and the second gas cavity 34, the first gas cavity 33 can provide the right force to the floating block 35 under the action of the pressure of the gas and transmits the right force to the movable turbine disc 21, and the left force provided by the gas to the movable turbine disc 21 and the static turbine disc 22 under the action of the compressed gas is counteracted. By the formula: f = p · s the optimum cross-sectional area of the slider 35 can be calculated so that the forces from the gas on the left and right sides of the moving turbine disk 21 are balanced. Let move the critical state that turbine disc 21 just is in contact with quiet turbine disc 22, can neither take place between the turbine disc 21 that moves this moment and the quiet turbine disc 22 because of the inseparable terminal surface that causes of pasting leaks, also can not cause the too tight friction that causes of pasting and generate heat, increase consumption.

The invention is described above with reference to the accompanying drawings, it is obvious that the invention is not limited to the above embodiments, and it is within the scope of the invention to adopt such insubstantial modifications of the inventive method concept and solution, or to apply the inventive concept and solution directly to other applications without such modifications.

Claims

1. A bidirectional floating pressing mechanism for reducing friction of a moving turbine disc comprises a cylindrical main bearing seat (1), and is characterized in that one end of the main bearing seat (1) is connected with a compression part (2), a pressing part (3) and a floating assembly (4) are arranged inside the main bearing seat (1), a main rotating shaft (11) is connected inside the main bearing seat (1) through a bearing, and a first high-pressure gas channel (12) is formed in the inner wall of the main bearing seat (1);

the compression component (2) comprises a moving turbine disc (21), the moving turbine disc (21) is fixed at one end of the main rotating shaft (11) far away from the radial plane of the main bearing seat (1), a static turbine disc (22) is coupled to one end of the dynamic turbine disc (21) far away from the main rotating shaft (11), the static turbine disc (22) is fixed on the shell of the main bearing seat (1), a high-pressure exhaust port (24) is arranged on the central axis of the radial plane of the static turbine disc (22), the outer peripheral surface of the static turbine disc (22) is provided with a low-pressure air suction port (23), a second high-pressure gas channel (25) is fixed on the outer peripheral surface of the static turbine disc (22), one end, far away from the moving turbine disc (21), of the second high-pressure gas channel (25) penetrates through the peripheral surface of the main bearing seat (1) and extends into the main bearing seat (1) to be communicated with the first high-pressure gas channel (12);

the pressing component (3) comprises a gap (31) formed between the inner wall of the main bearing seat (1) and the moving turbine disc (21), a floating block (35) is connected to the inside of the gap (31) in a sliding mode, the inside of the gap (31) is divided into a first air cavity (33) and a second air cavity (34) through the floating block (35), a fourth high-pressure air channel (32) is formed in a shell of the floating block (35), and two ends of the fourth high-pressure air channel (32) are communicated with the first air cavity (33) and the second air cavity (34) respectively; the floating assembly (4) comprises a floating block retainer (41), the floating block retainer (41) is fixed at one end, close to the power turbine disc (21), of the main rotating shaft (11), the floating block retainer (41) is located between the gap (31) and the inner wall of the main bearing seat (1), a third high-pressure gas channel (42) is formed in a shell of the floating block retainer (41), and two ends of the third high-pressure gas channel (42) are communicated with the second high-pressure gas channel (25) and the first gas cavity (33) respectively.

2. The bidirectional floating pressing mechanism for reducing friction of a moving turbine disk as claimed in claim 1, wherein an anti-rotation cylinder (43) is fixed to a surface of one side of the slider holder (41) close to the first air chamber (33).

3. The bidirectional floating pressing mechanism for reducing the friction of the power turbine disc as claimed in claim 2, wherein a pin hole (351) engaged with the rotation preventing column (43) is formed on the housing of the floating block (35).

4. The bidirectional floating pressing mechanism for reducing friction of a moving turbine disk according to claim 3, wherein a ripple spring (44) is arranged between the floating block holder (41) and the floating block (35), and the ripple spring (44) is fixed on one side surface of the floating block holder (41) close to the floating block (35).

5. The bidirectional floating pressing mechanism for reducing friction of a moving turbine disk as claimed in claim 4, wherein a balancing weight (6) is fixed on one side of the floating block retainer (41) far away from the moving turbine disk (21).

6. The bidirectional floating pressing mechanism for reducing friction of a dynamic turbine disk as claimed in claim 1, wherein the compression component (2) is connected with a sealing assembly (5), the sealing assembly (5) comprises a first O-shaped ring (51), a second O-shaped ring (52) and a third O-shaped ring (53), the first O-shaped ring (51) is embedded in the inner wall of one end of the first air cavity (33) far away from the second air cavity (34), the second O-shaped ring (52) is embedded in the outer circumferential surface of the floating block (35), and the third O-shaped ring (53) is embedded in the inner wall of one end of the second air cavity (34) far away from the first air cavity (33).

7. The bidirectional floating pressing mechanism for reducing friction of the moving turbine disc as claimed in claim 6, wherein a self-lubricating wear-resistant sealing strip (54) abuts against one side of the third O-shaped ring (53) close to the second O-shaped ring (52), and the self-lubricating wear-resistant sealing strip (54) is embedded in an inner wall of one end of the second air cavity (34) far away from the first air cavity (33).

8. The bidirectional floating pressing mechanism for reducing friction of a dynamic turbine disk as claimed in claim 1, wherein a plurality of anti-rotation eccentric pins (13) are fixed on the inner wall of the main bearing seat (1), and the plurality of anti-rotation eccentric pins (13) are arranged around the central axis of the radial plane of the main bearing seat (1) at equal intervals one by one and are parallel to the central axis.

9. The bi-directional floating clamping mechanism for reducing friction of a moving turbine disk as claimed in claim 1, wherein the outer surface of the floating block (35) is provided with an electroplated layer.