CN117231470A

CN117231470A - Gas bearing device of compressor and compressor

Info

Publication number: CN117231470A
Application number: CN202311505576.9A
Authority: CN
Inventors: 铁鹏; 陈海燕; 乔扬
Original assignee: Runa Smart Equipment Co Ltd
Current assignee: Runa Smart Equipment Co Ltd
Priority date: 2023-11-13
Filing date: 2023-11-13
Publication date: 2023-12-15

Abstract

The application discloses a gas bearing device of a compressor and the compressor, the gas bearing device comprises: a cylinder; the piston is arranged in the cylinder at least partially, the piston is movable relative to the cylinder along the axial direction of the cylinder, a compression cavity and a dynamic seal gap are formed between the piston and the cylinder, the compression cavity is located between the end wall of the piston, which is close to the cylinder, and the cylinder along the axial direction of the cylinder, the dynamic seal gap is located between the side wall of the piston and the cylinder, an air storage chamber is formed in the piston, an air vent group and an air outlet hole group are formed on the side wall of the piston, the air vent group and the air outlet hole group are both communicated with the air storage chamber and the dynamic seal gap, and the air outlet hole group is located on one side, which is far away from the compression cavity, of the air vent group along the axial direction of the cylinder. Through the cooperation of piston and cylinder, can provide a reliability height, simple structure's gas bearing device, can provide gas lubrication for between piston and the cylinder, reduce the friction of piston and cylinder, prolong the life of piston and cylinder, promote the life of compressor.

Description

Gas bearing device of compressor and compressor

Technical Field

The application relates to the field of compressors, in particular to a gas bearing device of a compressor and the compressor.

Background

In the related art, a piston and a cylinder of a compressor can be assembled generally by a gap sealing technique, and a gap between the piston and the cylinder is generally below 20 μm, and although a smaller gap seal can reduce leakage loss, friction between the piston and the cylinder is easily caused, resulting in a reduction in the life of the piston or the cylinder.

Disclosure of Invention

The present application aims to solve at least one of the technical problems existing in the prior art. Therefore, an object of the present application is to provide a gas bearing device for a compressor, which reduces friction between a piston and a cylinder and prolongs the service life of the piston and the cylinder.

The application also provides a compressor with the gas bearing device.

A gas bearing device of a compressor according to an embodiment of the present application includes: a cylinder; the piston is arranged in the cylinder at least partially, the piston is movable relative to the cylinder along the axial direction of the cylinder, a compression cavity and a dynamic seal gap are formed between the piston and the cylinder, the compression cavity is located between the end wall of the piston, which is close to the cylinder, and the cylinder along the axial direction of the cylinder, the dynamic seal gap is located between the side wall of the piston and the cylinder, an air storage chamber is formed in the piston, an air vent group and an air outlet hole group are formed on the side wall of the piston, the air vent group and the air outlet hole group are both communicated with the air storage chamber and the dynamic seal gap, and the air outlet hole group is located on one side, which is far away from the compression cavity, of the air vent group along the axial direction of the cylinder.

Therefore, through the cooperation of the piston and the air cylinder, the gas bearing device with high reliability and simple structure can be provided, a pressure gas film can be formed between the piston and the air cylinder, gas lubrication can be provided between the piston and the air cylinder, the piston and the air cylinder are spaced apart, friction between the piston and the air cylinder is reduced when the piston moves, and the setting of wearing parts can be reduced, so that the service lives of the piston and the air cylinder are prolonged, and the service life of the compressor is further prolonged.

In some embodiments of the present application, the air outlet hole group includes a plurality of first air floating holes, and the plurality of first air floating holes are arranged along a circumferential direction of the piston.

In some embodiments of the application, the first plurality of air bearing holes are evenly spaced along the circumference of the piston.

In some embodiments of the present application, the air outlet hole groups are multiple groups, and the multiple groups of air outlet hole groups are sequentially arranged along the axial direction of the air cylinder.

In some embodiments of the application, the plurality of groups of gas outlet holes are spaced apart in sequence along the axial direction of the cylinder.

In some embodiments of the present application, the vent group includes a plurality of second air-floating holes arranged along a circumferential direction of the piston.

In some embodiments of the application, the plurality of second air bearing holes are evenly spaced along the circumference of the piston.

In some embodiments of the application, the end wall is provided with an inlet valve which opens in one direction into the reservoir and the compression chamber so that gas in the reservoir flows into the compression chamber through the inlet valve.

In some embodiments of the application, an annular dividing wall is provided in the gas reservoir, the dividing wall being provided around the inlet valve and being fixed to the end wall, the dividing wall dividing the gas reservoir into a first gas chamber and a second gas chamber, the first gas chamber being located between the dividing wall and a side wall of the piston, the second gas chamber being provided in correspondence with the inlet valve.

In some embodiments of the application, the end of the piston remote from the cylinder is formed with a vent opening in the axial direction of the cylinder, the vent opening communicating with the air reservoir.

According to an embodiment of the application, a compressor comprises the gas bearing device of the compressor.

Additional aspects and advantages of the application will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the application.

Drawings

The foregoing and/or additional aspects and advantages of the application will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:

FIG. 1 is an enlarged schematic view of a portion of a gas bearing device according to a first embodiment of the present application;

FIG. 2 is a schematic diagram of the direction of flow of compressed exhaust process gas for a gas bearing device according to a first embodiment of the present application;

FIG. 3 is a schematic view of the direction of flow of gas during the inspiratory expansion process of a gas bearing device according to a first embodiment of the present application;

FIG. 4 is a schematic view of a gas bearing device provided with a second embodiment of a compressor according to an embodiment of the present application;

FIG. 5 is an enlarged partial view of a gas bearing assembly according to a second embodiment of the application;

fig. 6 is an enlarged view at a in fig. 4.

Reference numerals:

a gas bearing device 100;

a cylinder 11;

a piston 13; an end wall 1301; a sidewall 1302; a partition wall 1303;

a compression chamber 15;

a dynamic seal gap 17;

an air reservoir 19; a first gas chamber 1901; a second plenum 1902;

a vent group 21; a second air bearing hole 2101;

a gas outlet hole group 23; a first air bearing hole 2301;

an intake valve 25;

a vent open end 27;

a compressor 200.

Detailed Description

Embodiments of the present application are described in detail below, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to like or similar elements or elements having like or similar functions throughout. The embodiments described below by referring to the drawings are illustrative only and are not to be construed as limiting the application.

A gas bearing device 100 of a compressor 200 according to an embodiment of the present application is described below with reference to fig. 1 to 6.

As shown in fig. 1 to 3, a gas bearing device 100 of a compressor 200 according to an embodiment of the present application includes: a cylinder 11; the piston 13, at least part of the piston 13 is located in the cylinder 11, and is movable along the axial direction of the cylinder 11 relative to the cylinder 11, a compression cavity 15 and a dynamic seal gap 17 are formed between the piston 13 and the cylinder 11, the compression cavity 15 is located between the end wall 1301 of the piston 13, which is close to the cylinder 11, and the cylinder 11 along the axial direction of the cylinder 11, the dynamic seal gap 17 is located between the side wall 1302 of the piston 13 and the cylinder 11, an air storage chamber 19 is formed in the piston 13, and the side wall 1302 of the piston 13 is formed with a vent hole group 21 and an air outlet hole group 23, the vent hole group 21 and the air outlet hole group 23 are both communicated with the air storage chamber 19 and the dynamic seal gap 17, and the air outlet hole group 23 is located on one side of the vent hole group 21, which is far away from the compression cavity 15, along the axial direction of the cylinder 11.

Specifically, as shown in fig. 1 to 3, the cylinder 11 may define a groove structure with one end open, the piston 13 may be installed in the cylinder 11 from the open end of the groove structure, at least part of the piston 13 is disposed in the groove structure of the cylinder 11, the cylinder 11 is sleeved outside the piston 13, and the piston 13 is movable relative to the cylinder 11 along the axial direction of the cylinder 11, i.e., the X direction in fig. 1, the groove structure has a depth direction coincident with the axial direction of the cylinder 11, a compression chamber 15 and a dynamic seal gap 17 are formed between the piston 13 and the cylinder 11, the compression chamber 15 is located between the end wall 1301 of the piston 13 adjacent to the cylinder 11 and the cylinder 11 along the axial direction of the cylinder 11, and it is also understood that the compression chamber 15 is located between the bottom wall of the groove structure and the piston 13, the dynamic seal gap 17 is located between the side wall 1302 of the piston 13 and the cylinder 11, in other words, the dynamic seal gap 17 is located between the side wall 1302 of the piston 13 and the inner side wall of the groove structure.

The air storage chamber 19 is formed in the piston 13, and the side wall 1302 of the piston 13 is formed with the air vent group 21 and the air outlet hole group 23, it is also understood that the side wall 1302 of the air storage chamber 19 is formed with the air vent group 21 and the air outlet hole group 23, the air vent group 21 and the air outlet hole group 23 are both communicated with the air storage chamber 19 and the dynamic seal gap 17, along the axial direction of the cylinder 11, the air outlet hole group 23 is located at one side of the air vent group 21 away from the compression chamber 15, wherein the air storage chamber 19 can store high-pressure air required by air floatation, the high-pressure air can flow through the air vent group 21 and the air outlet hole group 23 to provide deviation rectifying force for the piston 13, and the number and the size of the air vent group 21 and the air outlet hole group 23 can be determined by the deviation rectifying force required by the piston 13.

When the compressor 200 works, the piston 13 makes periodic reciprocating motion in the cylinder 11 along the axial direction of the cylinder 11, the whole motion process can be divided into a compression exhaust process and an expansion suction process, the side wall 1302 of the piston 13 is provided with the vent hole group 21 and the air outlet hole group 23, so that the air pressure in the air storage chamber 19 is different from the air pressure at the dynamic sealing gap 17, and the pressure difference at the vent hole group 21 and the dynamic sealing gap 17 and the air outlet hole group 23 and the dynamic sealing gap 17 is different, thereby generating deviation correcting force in the radial direction of the piston 13, enabling the piston 13 to passively correct deviation, and further enabling the piston 13 and the cylinder 11 to be spaced.

Specifically, when the compressor 200 is operated, the gas bearing device 100 moves toward the compression chamber 15 side during the compression and exhaust process, the gas pressure in the compression chamber 15 becomes large, the gas in the compression chamber 15 flows toward the dynamic seal gap 17, the gas pressure in the compression chamber 15 is greater than the gas pressure in the dynamic seal gap 17, the gas pressure in the dynamic seal gap 17 near the compression chamber 15 side of the vent hole group 21 is greater than the gas pressure in the gas reservoir 19, and the gas pressure in the gas reservoir 19 is greater than the gas pressure in the dynamic seal gap 17 at the gas outlet hole group 23. Therefore, since the gas pressure in the compression chamber 15 is greater than the gas pressure in the dynamic seal gap 17 on the side of the vent hole group 21 close to the compression chamber 15, the high-pressure gas in the compression chamber 15 can flow into the dynamic seal gap 17, and since the gas pressure in the dynamic seal gap 17 on the side of the vent hole group 21 close to the compression chamber 15 is greater than the gas pressure in the gas storage chamber 19, a larger portion of the gas can flow from the vent hole group 21 into the gas storage chamber 19, and a smaller portion of the gas can flow along the dynamic seal gap 17 toward the gas outlet hole group 23. Because the gas pressure in the gas storage chamber 19 is larger than the gas pressure in the dynamic seal gap 17 at the gas outlet hole group 23, the gas can flow from the gas storage chamber 19 into the dynamic seal gap 17 at the gas outlet hole group 23, thereby forming air floatation, generating deviation correcting force in the radial direction of the piston 13, so that the piston 13 passively corrects the deviation, ensuring the centering of the piston 13, further enabling the piston 13 and the gas cylinder 11 to be coaxial, and eliminating friction between the piston 13 and the gas cylinder 11.

When the compressor 200 is operated, the piston 13 moves to the side far away from the compression chamber 15 in the air suction expansion process of the air bearing device 100, at this time, the air cylinder 11 is under negative pressure, and the air cylinder 11 sucks air through the air suction valve, so that the air pressure in the air storage chamber 19 is greater than the air pressure in the dynamic seal gap 17 at the air outlet hole group 23, the air pressure in the dynamic seal gap 17 at the air outlet hole group 23 is greater than the air pressure in the dynamic seal gap 17 of the vent hole group 21 near the compression chamber 15, and the air pressure in the dynamic seal gap 17 of the vent hole group 21 near the compression chamber 15 is greater than the air pressure in the compression chamber 15. Therefore, in the process of air suction expansion, the gas bearing device 100 can make the high-pressure gas stored in the air storage chamber 19 flow into the dynamic seal gap 17 through the vent hole group 21 and the air outlet hole group 23, so as to form air floatation, and generate deviation correcting force in the radial direction of the piston 13, so that the piston 13 passively corrects the deviation, the centering of the piston 13 is ensured, and further, the piston 13 and the air cylinder 11 can be coaxial, and friction between the piston 13 and the air cylinder 11 is eliminated.

Therefore, through the cooperation of the piston 13 and the cylinder 11, the side wall 1302 of the piston 13 is provided with the vent hole group 21 and the air outlet hole group 23, so that the gas bearing device 100 with high reliability and simple structure can be provided, a pressure gas film can be formed between the piston 13 and the cylinder 11, gas lubrication can be provided between the piston 13 and the cylinder 11, friction between the piston 13 and the cylinder 11 is reduced, the service lives of the piston 13 and the cylinder 11 are prolonged, and the service life of the compressor 200 is further prolonged.

In some embodiments of the present application, as shown in fig. 1-3, the air outlet hole group 23 may include a plurality of first air float holes 2301, and the plurality of first air float holes 2301 are arranged along the circumferential direction of the piston 13. By arranging the plurality of first air floatation holes 2301 and arranging the plurality of first air floatation holes 2301 along the circumferential direction of the piston 13, the air in the air storage chamber 19 can flow into the dynamic seal gap 17 through the plurality of first air floatation holes 2301 at the same time, so that air floatation can be formed along the circumferential direction of the piston 13, deviation correcting force is generated in the radial direction of the piston 13, the centering of the piston 13 is further ensured, the contact probability of the piston 13 and the cylinder 11 is further reduced, and the abrasion of the piston 13 and the cylinder 11 is reduced.

In some embodiments of the present application, as shown in fig. 1-3, the plurality of first air bearing holes 2301 may be evenly spaced along the circumference of the piston 13. By uniformly arranging the plurality of first air floatation holes 2301 at intervals along the circumferential direction of the piston 13, the air in the air storage chamber 19 can uniformly flow to the dynamic seal gap 17 along the radial direction of the piston 13 through the first air floatation holes 2301, so that the air floatation can be uniformly distributed along the circumferential direction of the piston 13, uniform deviation rectifying force is generated, and the centering of the piston 13 is further ensured.

In some embodiments of the present application, as shown in fig. 1 to 3, the air outlet hole groups 23 may be multiple groups, and the multiple groups of air outlet hole groups 23 are sequentially arranged along the axial direction of the cylinder 11. Through setting up the venthole group 23 into the multiunit, and multiunit venthole group 23 arranges in proper order along the axial direction of cylinder 11, can make the gas in the air receiver 19 flow to dynamic seal clearance 17 through multiunit venthole group 23 to can form the air supporting along the axial of piston 13, and make the air supporting arrange along the axial of cylinder 11, and then make the force of rectifying distribute along the axial of cylinder 11, further guarantee the centering of piston 13. The axial direction of the piston 13 coincides with the axial direction of the cylinder 11.

In some embodiments of the present application, as shown in fig. 1 to 3, a plurality of gas outlet hole groups 23 may be disposed at intervals in order along the axial direction of the cylinder 11. By arranging the plurality of groups of air outlet holes 23 at intervals in sequence along the axial direction of the cylinder 11, the deviation correcting force can be further distributed along the axial direction of the cylinder 11, and the neutrality of the piston 13 is further ensured.

In some embodiments of the present application, as shown in fig. 1 to 3, the vent group 21 may include a plurality of second air floating holes 2101, the plurality of second air floating holes 2101 being arranged along a circumferential direction of the piston 13. By providing the plurality of second air floating holes 2101 and arranging the plurality of second air floating holes 2101 along the circumferential direction of the piston 13, when the compressor 200 works, the gas bearing device 100 can enable the gas in the dynamic seal gap 17 to flow into the gas storage chamber 19 through the plurality of second air floating holes 2101 in the process of compressing and exhausting, so that the gas in the gas storage chamber 19 is conveniently supplemented. In the process of air suction expansion, the air bearing device 100 can enable the air in the air storage chamber 19 to flow to the dynamic seal gap 17 through the plurality of second air floatation holes 2101, so that air floatation is formed in the dynamic seal gap 17 at the vent hole group 21, deviation correction force is generated in the radial direction of the piston 13, and the neutrality of the piston 13 is ensured.

In some embodiments of the present application, as shown in fig. 1 to 3, the plurality of second air bearing holes 2101 may be uniformly spaced apart in the circumferential direction of the piston 13, and the spacing distance between adjacent two second air bearing holes 2101 is the same. By arranging the plurality of second air floating holes 2101 at equal intervals along the circumferential direction of the piston 13, when the compressor 200 works, the gas bearing device 100 can make the gas in the dynamic seal gap 17 flow to the gas storage chamber 19 along the radial direction of the piston 13 uniformly through the second air floating holes 2101 in the compression and exhaust process, so that the gas can be conveniently and uniformly supplemented into the gas storage chamber 19, and the gas pressure of each region in the gas storage chamber 19 can be the same or approximately the same. In the process of air suction expansion, the air bearing device 100 can enable the air in the air storage chamber 19 to uniformly flow into the dynamic seal gap 17 along the circumferential direction of the piston 13 through the plurality of second air floatation holes 2101, so that air floatation can be uniformly distributed in the circumferential direction of the piston 13, uniform deviation correcting force is generated, and the centering of the piston 13 is further ensured.

In some embodiments of the application, as shown in fig. 5, end wall 1301 may be provided with an intake valve 25, with intake valve 25 in unidirectional communication with reservoir 19 and compression chamber 15, such that gas in reservoir 19 flows into compression chamber 15 through intake valve 25. In this embodiment, the piston 13 is formed with an air inlet, the air inlet is communicated with the air storage chamber 19, and when the compressor 200 is operated, the air bearing device 100 flows into the air storage chamber 19 through the air inlet in the air suction expansion process, and by arranging the air inlet valve 25 on the end wall 1301, the air inlet valve 25 is opened, the air inlet valve 25 is in one-way communication with the air storage chamber 19 and the compression chamber 15, so that the air in the air storage chamber 19 can quickly flow into the compression chamber 15 through the air inlet valve 25, and the air suction efficiency of the air cylinder 11 is improved.

In some embodiments of the present application, as shown in fig. 5, an annular partition wall 1303 may be disposed in the air storage chamber 19, the partition wall 1303 being disposed around the air intake valve 25 and fixed to the end wall 1301, the partition wall 1303 dividing the air storage chamber 19 into a first air chamber 1901 and a second air chamber 1902, the first air chamber 1901 being located between the partition wall 1303 and the side wall 1302 of the piston 13, the second air chamber 1902 being disposed corresponding to the air intake valve 25. Specifically, as shown in fig. 5, an annular partition wall 1303 is provided in the air storage chamber 19, the partition wall 1303 is provided around the air intake valve 25, and the partition wall 1303 is fixed to the end wall 1301, the partition wall 1303 partitions the air storage chamber 19 into a first air chamber 1901 and a second air chamber 1902, the first air chamber 1901 is located between the partition wall 1303 and the side wall 1302 of the piston 13, the first air chamber 1901 can store high-pressure air required for air floatation, the second air chamber 1902 is provided in correspondence with the air intake valve 25, the air intake port of the piston 13 communicates with the second air chamber 1902, and during the air intake expansion of the air bearing device 100, air flows into the second air chamber 1902 through the air intake port, and air flowing into the second air chamber 1902 flows into the compression chamber 15 through the air intake valve 25.

Thus, the partition wall 1303 is provided around the intake valve 25 and fixed to the end wall 1301, the partition wall 1303 partitions the gas storage chamber 19 into a first gas chamber 1901 and a second gas chamber 1902, and the gas in the second gas chamber 1902 can flow into the compression chamber 15 through the intake valve 25, and the intake port can be provided in the piston 13, and the exhaust port is formed in the cylinder 11.

In some embodiments of the present application, as shown in fig. 6, the end of the piston 13 remote from the cylinder 11 in the axial direction of the cylinder 11 may be formed with a ventilation open end 27 (i.e., an intake port in the above embodiment), the ventilation open end 27 being in communication with the air reservoir 19. Further, the vented open end 27 communicates with a second plenum 1902 within the air reservoir 19. Thus, by providing the ventilation open end 27, the ventilation open end 27 communicates with the second air chamber 1902 of the air receiver 19, the ventilation open end 27 also communicates with the back pressure chamber, and during the inhalation expansion of the gas bearing device 100, the gas at the back pressure chamber flows into the second air chamber 1902 through the ventilation open end 27, and the gas flowing into the second air chamber 1902 flows into the compression chamber 15 through the intake valve 25.

The gas bearing device 100 of the application provides a gas bearing device 100 with high reliability and simple structure, which provides gas lubrication between the piston 13 and the cylinder 11 and prolongs the service life of the piston 13 and the cylinder 11.

The first air bearing hole 2301, the second air bearing hole 2101 and the dynamic seal gap 17 of the air bearing device 100 of the present application have small dimensions, which are less than 20 μm, and are difficult to clearly display. A schematic diagram of the gas bearing device 100 with an enlarged size of the dynamic seal gap 17 is shown in fig. 1. The gas bearing device 100 comprises a piston 13 and a cylinder 11. Wherein a closed space can be formed inside the piston 13, namely an air storage chamber 19, and the air storage chamber 19 is used for storing high-pressure working medium (namely high-pressure gas in the embodiment) required by air floatation; the side wall 1302 of the piston 13 is provided with a plurality of first air floatation holes 2301 and a plurality of second air floatation holes 2101, the high-pressure working medium flows through the plurality of first air floatation holes 2301 and the plurality of second air floatation holes 2101 to provide deviation rectifying supporting force for the piston 13, and the number and the size of the plurality of first air floatation holes 2301 and the plurality of second air floatation holes 2101 are determined by the deviation rectifying force required by the piston 13; between the inner wall of the cylinder 11 and the side wall 1302 of the piston 13 is a dynamic seal gap 17, which is typically only 0.01mm; a compression chamber 15 is formed between cylinder 11 and piston 13 adjacent end wall 1301 of cylinder 11 for compressing exhaust gases and expanding intake gases.

The gas bearing device 100 is derived from the fact that the piston 13 is eccentric in the radial direction, so that the pressure difference between each air floatation hole and the dynamic seal gap 17 in the circumferential direction is different, and a radial deviation rectifying force is generated, so that the piston 13 is passively rectified, and the purpose that the piston 13 and the cylinder 11 are coaxial is achieved. The magnitude of this aerodynamic force is thus dependent on the maximum difference in aerodynamic force required to overcome the eccentricity of the piston 13, which, as known from classical mechanics, is related to the pressure difference at each of the air bearing holes in the circumferential direction. Taking fig. 2 as an example, P2, P4, and P5 are gas pressures in the dynamic seal gap 17, P3 is the pressure in the air storage chamber 19, and under the same size condition, the gas force value provided by the gas bearing device 100 is derived from the pressure difference between P3 and P2 (P4/P5). In view of the fact that the change rule of the pressure values of P2, P4 and P5 is almost constant under the condition of the same size, at this time, the deviation rectifying force provided by the gas bearing device 100 directly depends on the pressure value in the gas storage chamber 19, i.e. the pressure value in the gas storage chamber 19 can be designed and adjusted according to the requirement of the deviation rectifying force.

According to the gas bearing device 100, due to the fact that the piston 13 is eccentric in the radial direction, the pressure difference between the gas outlet hole group 23 and the vent hole group 21 in the circumferential direction of the piston 13 and the dynamic seal gap 17 is different, so that the piston 13 generates radial deviation correcting force, the piston 13 is passively corrected, and the purpose that the piston 13 and the cylinder 11 are coaxial is achieved. The magnitude of this aerodynamic force (i.e. the correction force in the above embodiment) is therefore dependent on the maximum gas force difference required to overcome the eccentricity of the piston 13. As known from classical mechanics, this gas force difference is related to the pressure difference at each of the sets of gas outlet holes 23, the set of gas vent holes 21 in the circumferential direction. Taking fig. 2 as an example, under the condition of the same size, the deviation rectifying force provided by the gas bearing device 100 is derived from the pressure difference between the gas pressure in the dynamic seal gap 17 and the gas pressure in the gas storage chamber 19, and the change rule of the gas pressure in the dynamic seal gap 17 is almost constant, so that the deviation rectifying force provided by the gas bearing device 100 directly depends on the gas pressure in the gas storage chamber 19, i.e. the gas pressure value in the gas storage chamber 19 can be designed and adjusted according to the requirement of the deviation rectifying force.

When the compressor 200 is operated, the piston 13 is periodically reciprocated in the cylinder 11, and the entire movement can be divided into a compression discharge process and an expansion suction process. The operation of the gas bearing device 100 in these two processes will be described in detail below. Also, since the partial area is undersized, only the schematic is used as illustration of the process principle description.

Further, taking the positioning of the gas bearing device 100 according to fig. 2 and 3 as an example, for convenience of description, define P1 as the gas pressure in the compression chamber 15, which is determined by the system design; p2 is the gas pressure of the second air-floating hole 2101 at the side close to the compression chamber 15 in the dynamic seal gap 17; p4 and P5 are the gas pressure of the first air floatation hole 2301 in the dynamic seal gap 17, and because the dynamic seal gap 17 is small, the pressure values of P2, P4 and P5 are greatly different, and in FIG. 2, the pressure value of P2 is close to P1, and the pressure value of P5 is close to P6; p3 is the gas pressure in the gas storage chamber 19, and can be designed according to the required deviation correcting force; p6 is the pressure of the back pressure chamber, determined by the system design, and is approximately constant.

When the compressor 200 is operated, the gas bearing device 100 compresses the gas in the cylinder 11 during the compression and exhaustion, as shown in fig. 2, when the gas bearing device 100 is placed in the position of fig. 2, the piston 13 moves rightward. At this time, the relation of the pressure values is that P1 > P2 > P3 > P4 > P5 > P6, and the gas flow in the gas bearing device 100 is shown by the arrow, after the high-pressure gas from the compression chamber 15 enters the dynamic seal gap 17, the gas with more share flows into the gas storage chamber 19 from the second air floatation hole 2101 due to the pressure difference between P2 and P3, and the gas with less share flows leftwards along the dynamic seal gap 17; because P3 > P4 > P5, in the first air-float hole 2301, air flows from the air reservoir 19 into the dynamic seal gap 17 to form air-float, generating air-float force (i.e., correction force in the above embodiment), maintaining the centering of the piston 13, and eliminating friction between the piston 13 and the cylinder 11. The second air floatation hole 2101 takes responsibility of supplementing air to the air storage chamber 19, and by calculating key parameters such as the air floatation force (i.e. the deviation correcting force in the embodiment) and the positions of the air vent group 21 and the air outlet group 23, a proper structure can be obtained, so that the air pressure and the air storage capacity in the air storage chamber 19 are ensured.

Further, according to the first embodiment of the present application, the test of the working gas bearing device 100 of the compressor 200 during the compression exhaust process is performed, and the pressures at the above points are further described. In the test, the compression chamber 15 was set at a pressure of 1.8MPa, the back pressure chamber was set at a pressure of 0.4MPa, and the dynamic seal gap 17 was set at 0.01mm along the radial width of the piston 13 and at 80mm along the axial length of the piston 13. Since the dynamic seal gap 17 is very small, the gas pressure in the dynamic seal gap 17 shows a sharp decrease trend along the direction from the compression chamber 15 to the back pressure chamber, from about 1.778MPa to about 0.413MPa, and a decrease of up to 1.3MPa. The second air-floating hole 2101 is located in a relatively high-pressure area on the side close to the compression chamber 15 where the pressure is higher than the gas pressure in the gas storage chamber 19, whereby the gas in the gas storage chamber 19 can be replenished through the second air-floating hole 2101 of the high-pressure area. The first air floatation hole 2301 is located in a relatively low pressure area near the back pressure chamber side where the pressure is lower than the pressure in the air storage chamber 19, and can provide air floatation force (i.e., correction force in the above embodiment) to the piston 13. As described above, the position of the second air-floating hole 2101 can be adjusted according to the air-floating force (i.e., the deviation correcting force in the above embodiment) required by the piston 13, so as to adjust the air pressure in the air storage chamber 19, so that the air pressure in the air storage chamber 19 is higher than the air pressure in the first air-floating hole 2301, thereby providing the air-floating force (i.e., the deviation correcting force in the above embodiment) to the piston 13.

During the compression and exhaust process, the gas in the dynamic seal gap 17 at the air floatation hole in the high-pressure area flows into the gas storage chamber 19 through the air floatation hole, and the gas in the gas storage chamber 19 flows into the dynamic seal gap 17 through the air floatation hole.

When the compressor 200 is operated, as shown in fig. 3, the piston 13 moves leftwards during the air suction and expansion process when the air bearing device 100 is placed at the position shown in fig. 3, negative pressure is applied to the cylinder 11, the cylinder 11 sucks air through the air suction valve, the relation of the pressure values is P3 > P4 > P5 > P2 > p1=p6, at this time, the air in the air bearing device 100 flows as shown by the arrow, the high-pressure air stored in the air storage chamber 19 flows into the dynamic seal gap 17 through the first air floatation hole 2301 and the second air floatation hole 2101, air floatation is formed, deviation rectifying force is generated, the centering of the piston 13 is maintained, and friction between the piston 13 and the cylinder 11 is eliminated. Because of the low leak rate of the seal, the gas stored in the suitable reservoir 19 ensures a gas consumption during the whole inspiration.

Because the second air floatation holes 2101 have the dual functions of air supply and air floatation, during design, the required deviation rectifying force of the piston 13 can be determined, the structures and the number of the air outlet hole groups 23 and the air vent hole groups 21, the internal and external pressure difference of the piston 13 and the like are determined according to the required deviation rectifying force, and then the position and the structure of the second air floatation holes 2101 are determined according to the required air pressure in the air storage chamber 19; when high pressure is required at the second air-float hole 2101, the second air-float hole 2101 may be disposed closer to the compression chamber 15; the second air bearing holes 2101 may be provided away from the compression chamber 15 when high pressure is not required.

In the gas bearing device 100 of the present application, as shown in fig. 4, the end wall 1301 of the piston 13 is provided with the intake valve 25, and the intake mode of the cylinder 11 may be changed to the intake from the intake valve 25 of the piston 13, and a partially enlarged schematic view thereof is shown in fig. 5. In fig. 5, the piston 13 is changed to a double-layer hollow structure, and the air storage chamber 19 is partitioned into a first air chamber 1901 and a second air chamber 1902 by providing an annular partition wall 1303 in the air storage chamber 19, and providing the piston 13 to the double-layer hollow structure. Wherein, the middle hollow structure forms a second air chamber 1902, when the gas bearing device 100 is placed according to the position of fig. 5, the left end of the second air chamber 1902 is communicated with the back pressure cavity, and the gas can be directly supplemented from the back pressure cavity; the end wall 1301 of the piston 13 is provided with an intake valve 25, and during the intake expansion phase, the intake valve 25 is open and back pressure chamber gas passes through the second chamber 1902 and into the cylinder 11 via the open intake valve 25. The internal cavity structure at the periphery of the second air chamber 1902 forms a first air chamber 1901, which can store high-pressure air needed by air floatation, and functions as an air bearing, the functions and the processes of which are as described above, and the description is omitted for avoiding redundancy.

In the related art, the piston 13 can only be used as the air storage chamber 19 for air floatation, and the air inlet and the air outlet of the cylinder 11 are located on the same component, and at this time, the high-temperature and high-pressure air exhaust in the air exhaust process can affect the air suction process of the cylinder 11, so that the air suction efficiency of the cylinder 11 is reduced. By adopting the double-layer hollow structure piston 13, the piston 13 can be used as the air storage chamber 19 for forming air floatation, and can also be used for sucking air of the air cylinder 11, the air inlet and the air inlet valve 25 are arranged on the piston 13, the air outlet is arranged on the air cylinder 11, the air inlet valve 25 and the air outlet are arranged on different components, and the air suction process and the air discharge process are separated, so that the influence of the compression air discharge process on expansion air suction can be avoided, and the air suction efficiency of the expansion air suction process of the air cylinder 11 is ensured.

A compressor 200 according to an embodiment of the present application includes the gas bearing device 100 of the compressor 200 described above. It should be noted that the above explanation of the embodiments and advantageous effects of the gas bearing device 100 is also applicable to the compressor 200 according to the embodiment of the present application, and is not developed in detail herein to avoid redundancy.

In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present application and simplifying the description, and do not indicate or imply that the device or element being 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 application.

In the description of the application, a "first feature" or "second feature" may include one or more of such features.

In the description of the present application, "plurality" means two or more.

In the description of the application, a first feature "above" or "below" a second feature may include both the first and second features being in direct contact, and may also include the first and second features not being in direct contact but being in contact with each other by another feature therebetween.

In the description of the application, a first feature being "above," "over" and "on" a second feature includes the first feature being directly above and obliquely above the second feature, or simply indicates that the first feature is higher in level than the second feature.

In the description of the present specification, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the application. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

While embodiments of the present application have been shown and described, it will be understood by those of ordinary skill in the art that: many changes, modifications, substitutions and variations may be made to the embodiments without departing from the spirit and principles of the application, the scope of which is defined by the claims and their equivalents.

Claims

1. A gas bearing device for a compressor, comprising:

a cylinder;

the piston, at least part of piston is located in the cylinder, and along the axial of cylinder is relative the cylinder is movable, the piston with be formed with compression chamber and the dynamic seal clearance of intercommunication between the cylinder, along the axial of cylinder the compression chamber is located the piston is close to the end wall of cylinder with between the cylinder, the dynamic seal clearance is located the lateral wall of piston with between the cylinder, be formed with the air receiver in the piston, just the lateral wall of piston is formed with air vent group and venthole group, air vent group with the venthole group all communicates the air receiver with the dynamic seal clearance, along the axial direction of cylinder, the venthole group is located the air vent group is kept away from one side of compression chamber.

2. The gas bearing device of a compressor according to claim 1, wherein the gas outlet hole group includes a plurality of first gas float holes, the plurality of first gas float holes being arranged along a circumferential direction of the piston.

3. The gas bearing device of a compressor of claim 2, wherein a plurality of the first air bearing holes are uniformly spaced apart along a circumferential direction of the piston.

4. The gas bearing device of a compressor according to claim 1, wherein the gas outlet hole groups are plural groups, and plural groups of the gas outlet hole groups are arranged in order along an axial direction of the cylinder.

5. A gas bearing device of a compressor according to claim 4, wherein a plurality of said groups of gas outlet holes are provided at intervals in sequence in an axial direction of said cylinder.

6. The gas bearing device of a compressor according to claim 1, wherein the vent group includes a plurality of second air-floating holes, the plurality of second air-floating holes being arranged along a circumferential direction of the piston.

7. The gas bearing device of a compressor of claim 6, wherein a plurality of the second air bearing holes are uniformly spaced apart along a circumferential direction of the piston.

8. A gas bearing arrangement for a compressor according to any one of claims 1 to 7, wherein the end wall is provided with an inlet valve which unidirectionally opens the reservoir and the compression chamber so that gas in the reservoir flows into the compression chamber through the inlet valve.

9. The gas bearing device of claim 8, wherein an annular partition wall is provided in the gas storage chamber, the partition wall being provided around the intake valve and fixed to the end wall, the partition wall partitioning the gas storage chamber into a first gas chamber and a second gas chamber, the first gas chamber being located between the partition wall and a side wall of the piston, the second gas chamber being provided in correspondence with the intake valve.

10. A gas bearing arrangement for a compressor according to claim 8, wherein the end of the piston remote from the cylinder is formed with a vent opening in the axial direction of the cylinder, the vent opening communicating with the gas reservoir.

11. A compressor, characterized by comprising a gas bearing arrangement of a compressor according to any one of claims 1-10.