Compression cylinder and compressor

Abstract

A high-pressure cavity is formed in an air cylinder of the compression cylinder, a hydrostatic bearing used for supporting a piston is arranged on the inner wall of the air cylinder, a first air gap is formed between the inner circumferential wall of the hydrostatic bearing and the outer circumferential wall of the piston, a flow controller is arranged on the hydrostatic bearing, and a second air gap is formed between the inner circumferential wall of the hydrostatic bearing and the outer circumferential wall of the piston. An airflow channel communicated with the high-pressure cavity is formed in the cylinder wall of the air cylinder, and the high-pressure cavity, the airflow channel, the throttler and the first air gap are sequentially communicated. According to the compression cylinder and the compressor, high-pressure gas in the high-pressure cavity can be conveyed to the throttler through the airflow channel, the throttler depressurizes the high-pressure gas and conveys the high-pressure gas to the position between the hydrostatic bearing and the piston, so that an air gap layer is formed between the hydrostatic bearing and the piston, and the piston is supported through the air gap layer; therefore, abrasion of the piston surface and the cylinder inner wall is reduced, and compression efficiency of the compressor is improved.

Description

Technical Field

[0001] The present invention belongs to the technical field of bearings, and more specifically, relates to a compression cylinder and a compressor. Background Art

[0002] In a reciprocating compressor, a permanent magnet motor drives the crankshaft to rotate, and a piston is connected to the crankshaft. The piston moves inside the cylinder to compress the gas. Usually, the air intake and exhaust ports of the cylinder are set at the cylinder head. Low-pressure gas enters the cylinder from the air intake port, and high-pressure gas exits the cylinder from the exhaust port. Therefore, the movement of the piston inside the cylinder of the reciprocating compressor compresses the gas, thereby increasing the gas pressure.

[0003] One technical challenge that needs to be overcome in this type of reciprocating compressor is to reduce the direct contact between the piston and the cylinder. Specifically, due to the relative motion between the piston and the cylinder, dry friction occurs when the piston and the cylinder come into direct contact. Dry friction not only easily damages the cylinder, but also reduces the compression efficiency of the compressor. At present, a commonly used method to reduce the direct contact between the piston and the cylinder is to form an oil film between the cylinder and the piston to prevent the piston and the cylinder from wearing out prematurely. However, during the movement of the piston, the shaking of the piston may make the oil film thinner, or even cause the piston to come into direct contact with the cylinder, which still causes wear on the piston and the cylinder. Summary of the invention

[0004] The purpose of the embodiments of the present invention is to provide a compression cylinder and a compressor to solve the technical problem in the prior art that the cylinder body and the piston are easily worn, resulting in reduced compression efficiency.

[0005] To achieve the above-mentioned purpose, the technical solution adopted by the present invention is: to provide a compression cylinder, including a cylinder and a piston arranged in the cylinder, the piston can move relative to the cylinder, the interior of the cylinder has a high-pressure chamber for compressing gas, a hydrostatic bearing for supporting the piston is arranged on the inner wall of the cylinder, a first air gap is provided between the inner peripheral wall of the hydrostatic bearing and the outer peripheral wall of the piston, a throttle is provided on the hydrostatic bearing, and the cylinder wall of the cylinder has an air flow channel connected to the high-pressure chamber, and the high-pressure chamber, the air flow channel, the throttle and the first air gap are connected in sequence.

[0006] Optionally, a buffer chamber is further provided in the cylinder wall of the cylinder, and the high-pressure chamber, the buffer chamber and the air flow channel are connected in sequence.

[0007] Optionally, the cylinder includes a cylinder body having an opening and a cylinder cover arranged at the opening, the cylinder cover is provided with a first air hole and a second air hole, and the buffer chamber is arranged in the cylinder head, the high-pressure chamber is connected with the buffer chamber through the first air hole, and the air flow channel is connected with the buffer chamber through the second air hole.

[0008] Optionally, the cylinder body has the air flow channel, one end of the air flow channel is located at the end of the cylinder body having the opening, and the other end of the air flow channel extends to the outer peripheral wall of the static pressure bearing.

[0009] Optionally, the air flow channel is extended along the axial direction of the cylinder body, and a connecting hole is provided on the inner wall of the cylinder body, one end of the connecting hole is connected to the air flow channel, and the other end of the connecting hole passes through the inner wall of the cylinder body to the outer peripheral wall of the static pressure bearing and is connected to the throttle.

[0010] Optionally, the hydrostatic bearing is fixed to the inner wall of the cylinder, the hydrostatic bearing has mounting holes at both ends respectively penetrating its inner circumferential wall and its outer circumferential wall, the throttle is fixed in the mounting hole, and a second air gap is provided between the outer circumferential wall of the hydrostatic bearing and the inner circumferential wall of the cylinder body, and the second air gap is connected to the airflow channel.

[0011] Optionally, at least two sealing structures are arranged between the outer circumferential wall of the hydrostatic bearing and the inner circumferential wall of the cylinder, wherein the two sealing structures are respectively located at the axial ends of the hydrostatic bearing, so that the two sealing structures seal the axial ends of the second air gap, and the throttle is located between the two sealing structures.

[0012] Optionally, the outer peripheral wall of the hydrostatic bearing is concave to form a sink groove, the inner wall of the sink groove and the inner peripheral wall of the cylinder body form the second air gap, and the mounting holes are all opened on the bottom wall of the sink groove.

[0013] Optionally, the thickness of the hydrostatic bearing at the recess is greater than the axial length of the throttle.

[0014] Optionally, a plurality of throttle assemblies are sequentially spaced apart along the axial direction of the hydrostatic bearing, and the throttle assembly includes a plurality of throttles distributed along the circumference of the hydrostatic bearing.

[0015] Optionally, the throttle has a throttling hole arranged along its axial direction, and the throttling hole includes an air inlet section, a neck section and an air outlet section connected in sequence, the air outlet section is arranged in a conical shape, and the aperture of the neck section is smaller than the aperture of the air inlet section and smaller than the aperture of the air outlet section.

[0016] Optionally, the cone angle of the air outlet section ranges from 90° to 120°.

[0017] The present invention also provides a compressor, comprising the above-mentioned compression cylinder.

[0018] The compression cylinder and compressor provided by the present invention have the following beneficial effects: compared with the prior art, a high-pressure chamber is formed between the cylinder and the piston of the compression cylinder of the present invention, a hydrostatic bearing is arranged at the inner wall of the cylinder, and a throttle is arranged on the hydrostatic bearing. An airflow channel is arranged in the cylinder wall of the cylinder, and the high-pressure chamber, the airflow channel and the throttle are connected in sequence, so that the high-pressure gas in the high-pressure chamber can be transported to the throttle through the airflow channel, and the throttle reduces the pressure of the high-pressure gas and transports it to the first air gap between the hydrostatic bearing and the piston, so that a gas cushion is formed between the hydrostatic bearing and the piston, and the piston is supported by the gas filled in the first air gap, so that the piston and the inner wall of the cylinder are prevented from colliding and contacting with each other, thereby reducing the wear of the piston surface and the inner wall of the cylinder, and improving the compression efficiency of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings in the following description are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

[0020] Figure 1 A partial structural diagram of a compressor provided by an embodiment of the present invention;

[0021] Figure 2 for Figure 1 The enlarged structure diagram at A in the middle;

[0022] Figure 3 A cross-sectional view of a hydrostatic bearing provided by an embodiment of the present invention;

[0023] Figure 4 for Figure 3 Sectional view along line BB;

[0024] Figure 5 A cross-sectional view of a throttle provided in an embodiment of the present invention.

[0025] Among them, the reference numerals in the figure are:

[0026] 1-compression cylinder; 11-cylinder; 111-cylinder body; 112-cylinder head; 113-buffer chamber; 114-air flow channel; 115-second air hole; 116-annular groove; 117-connecting hole; 12-piston; 13-high-pressure chamber; 14-static bearing; 141-sinking groove; 142-mounting hole; 143-first sealing groove; 15-throttle; 150-throttle hole; 151-intake section; 152-neck section; 153-exhaust section; 16-sealing structure; 17-first air gap; 2-motor; 3-crankshaft. DETAILED DESCRIPTION

[0027] In order to make the technical problems, technical solutions and beneficial effects to be solved by the present invention more clearly understood, the present invention is further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0028] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it can be directly on the other element or indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or indirectly connected to the other element.

[0029] It should be understood that the orientation or position relationship indicated by terms such as "length", "width", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside" and "outside" are based on the orientation or position relationship shown in the drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operate in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0030] In addition, the terms "first" and "second" are used for descriptive purposes only and should not be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, the features defined as "first" and "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, the meaning of "plurality" is two or more, unless otherwise clearly and specifically defined.

[0031] The compressor is a relatively important component in heat exchange equipment such as refrigerators and air conditioners. The compressor compresses the gaseous refrigerant into a high-temperature and high-pressure gas, and sends it to the condenser for condensation. After condensation, the refrigerant becomes liquid. The liquid refrigerant is throttled and reduced in pressure by the throttling component (expansion valve) to become a low-temperature and low-pressure gas-liquid mixture. It absorbs heat from the air through the evaporator and vaporizes into a gas, and then returns to the compressor for further compression, and continues to circulate for refrigeration. Therefore, the compressor is the core component of the refrigeration equipment. The compressor includes a motor 2, a crankshaft 3 and a compression cylinder 1. The motor 2 drives the compression cylinder 1 to work and compress the gaseous refrigerant.

[0032] See also Figure 2The compression cylinder 1 includes a piston 12 and a cylinder 11. The piston 12 is arranged inside the cylinder 11, and the piston 12 can move relative to the cylinder 11. During the movement of the piston 12 relative to the cylinder 11, the gas in the cylinder 11 will be continuously compressed to form high-pressure gas, and then the high-pressure gas will be output to the condenser and other structural parts. The cylinder 11 has a high-pressure chamber 13 for compressing gas inside. In order to ensure that the reciprocating movement of the piston 12 can smoothly pressurize the gas in the high-pressure chamber 13, the high-pressure chamber 13 needs to be in a relatively sealed state, that is, the gap between the piston 12 and the cylinder 11 needs to be set very small or no gap. Therefore, during the movement of the piston 12, dry friction is easily generated between the piston 12 and the cylinder 11, and the outer side of the piston 12 and the inner wall of the cylinder 11 will wear quickly, resulting in the gap between the piston 12 and the cylinder 11 becoming larger and larger, the airtightness of the high-pressure chamber 13 is gradually weakened, and the compression efficiency is gradually reduced. In order to overcome the problem that the piston 12 and the cylinder 11 are prone to dry friction, the present invention proposes a new compression cylinder 1.

[0033] The compression cylinder 1 provided in the embodiment of the present invention is now described.

[0034] See also Figure 2 The compression cylinder 1 includes a cylinder 11, a piston 12 and a hydrostatic bearing 14.

[0035] The cylinder 11 is a structure with a cavity inside, and the cylinder 11 provides a compression container for gas compression.

[0036] The piston 12 is arranged inside the cylinder 11, and the piston 12 can move relative to the cylinder 11. The piston 12 divides the cavity inside the cylinder 11 into at least a high-pressure chamber 13. When the piston 12 moves in a first direction, the volume of the high-pressure chamber 13 increases, and the gas enters the high-pressure chamber 13 at the same time. When the piston 12 moves in a second direction, the volume of the high-pressure chamber 13 decreases. At this time, the high-pressure chamber 13 is in a closed state, and the movement of the piston 12 compresses the gas in the high-pressure chamber 13.

[0037] The hydrostatic bearing 14 is disposed at the inner wall of the cylinder 11, and is used to support the piston 12, reducing the possibility of contact between the piston 12 and the cylinder 11. A first air gap 17 is provided between the inner peripheral wall of the hydrostatic bearing 14 and the outer peripheral wall of the piston 12. By introducing gas into the first air gap 17, a gas cushion is formed between the hydrostatic bearing 14 and the piston 12, so that the piston 12 is suspended inside the cylinder 11, reducing the possibility of contact between the piston 12 and the cylinder 11, and between the piston 12 and the hydrostatic bearing 14.

[0038] Specifically, a throttle 15 is provided on the hydrostatic bearing 14, an air flow channel 114 is provided in the cylinder wall of the cylinder 11, the high pressure chamber 13, the air flow channel 114, the throttle 15 and the first air gap 17 are connected in sequence, one end of the throttle 15 is connected with the high pressure chamber 13 through the air flow channel 114, and the other end of the throttle 15 is used to transport the gas in the air flow channel 114 to between the hydrostatic bearing 14 and the piston 12. In other words, the gas in the high pressure chamber 13 is transported to one end of the throttle 15 through the air flow channel 114, and the throttle 15 can reduce the pressure of the high pressure gas, and then transport the reduced pressure gas to the first air gap 17 between the hydrostatic bearing 14 and the piston 12, so that a gas cushion is formed between the hydrostatic bearing 14 and the piston 12, and then the hydrostatic bearing 14 forms a gas hydrostatic support for the piston 12.

[0039] In the compression cylinder 1 in the above embodiment, a high-pressure chamber 13 is formed between the cylinder 11 and the piston 12, a hydrostatic bearing 14 is provided on the inner wall of the cylinder 11, and a throttle 15 is provided on the hydrostatic bearing 14. An air flow channel 114 is provided in the cylinder wall of the cylinder 11, and the high-pressure chamber 13, the air flow channel 114 and the throttle 15 are sequentially connected, so that the high-pressure gas in the high-pressure chamber 13 can be transported to the throttle 15 through the air flow channel 114, and the throttle 15 reduces the pressure of the high-pressure gas and transports it to the first air gap 17 between the hydrostatic bearing 14 and the piston 12, so that a gas cushion is formed between the hydrostatic bearing 14 and the piston 12, and the piston 12 is supported by the gas filled in the first air gap 17, so that the piston 12 and the cylinder 11 are prevented from colliding and contacting each other, thereby reducing the wear of the surface of the piston 12 and the inner wall of the cylinder 11, and improving the compression efficiency of the compressor.

[0040] It should be noted that the throttle 15 has an inlet end and an outlet end. Only when the gas pressure at the inlet end of the throttle 15 is greater than the gas pressure at the outlet end, the gas can flow from the inlet end of the throttle 15 to the outlet end, and the throttle 15 is in a conducting state. When the gas pressure at the inlet end of the throttle 15 is less than or equal to the gas pressure at the outlet end, the throttle 15 is in a closed state, that is, the high-pressure gas cannot be transported from the outlet end of the throttle 15 to its inlet end, and the throttle 15 is in a cut-off state. The inlet end of the throttle 15 faces the airflow channel 114 and is connected to the airflow channel 114. The other end of the throttle 15 faces the piston 12 or the high-pressure chamber 13. Since the piston 12 moves continuously in the cylinder 11, the piston 12 is adjacent to the throttle 15 at some times and not adjacent to the throttle 15 at some times. The piston 12 is adjacent to the throttle 15, which means that the outer peripheral wall of the piston 12 is adjacent to the gas outlet end of the throttle 15, and the gap therebetween is very small, usually less than 5 mm.

[0041] In some embodiments of the present invention, the piston 12 rotates inside the cylinder 11, and the piston 12 divides the cylinder 11 into a high-pressure chamber 13 and a low-pressure chamber. When the piston 12 rotates one circle, the gas in the high-pressure chamber 13 can be compressed. The piston 12 rotates relative to the cylinder 11, and the static pressure bearing 14 is fixed to the cylinder 11. In other words, the piston 12 can rotate relative to the static pressure bearing 14. When the piston 12 rotates to be adjacent to the throttle 15, the gas pressure at the inlet end of the throttle 15 is greater than the gas pressure at the outlet end of the throttle 15, and the gas enters between the piston 12 and the static pressure bearing 14 through the air flow channel 114 and the throttle 15 to form a gas cushion. When the piston 12 rotates to be not adjacent to the throttle 15, the outlet end of the throttle 15 faces the high-pressure chamber 13, and the gas pressure at the inlet end of the throttle 15 is less than the gas pressure at the outlet end of the throttle 15, and the high-pressure gas in the high-pressure chamber 13 will not leak from the throttle 15.

[0042] In some embodiments of the present invention, the piston 12 performs linear reciprocating motion inside the cylinder 11. Each time the piston 12 performs linear reciprocating motion, the gas in the high-pressure chamber 13 can be compressed. When the piston 12 moves to be adjacent to the throttle 15, the gas pressure at the inlet end of the throttle 15 is greater than the gas pressure at the outlet end of the throttle 15. The gas enters between the piston 12 and the static pressure bearing 14 through the air flow channel 114 and the throttle 15 to form a gas cushion. When the piston 12 moves to be not adjacent to the throttle 15, the outlet end of the throttle 15 faces the high-pressure chamber 13. The gas pressure at the inlet end of the throttle 15 is less than the gas pressure at the outlet end of the throttle 15. The high-pressure gas in the high-pressure chamber 13 will not leak from the throttle 15.

[0043] In some embodiments of the present invention, see Figure 2 A buffer chamber 113 is provided in the cylinder wall of the cylinder 11, and the high-pressure chamber 13, the buffer chamber 113 and the air flow channel 114 are connected in sequence. The buffer chamber 113 can be provided on the cylinder body 111 of the cylinder 11 or on the cylinder head 112 of the cylinder 11. By providing the buffer chamber 113, the gas in the high-pressure chamber 13 can be buffered in the buffer chamber 113. When the piston 12 moves to be adjacent to the throttle 15, the gas in the buffer chamber 113 will quickly pass through the air flow channel 114 and the throttle 15 and enter between the piston 12 and the static pressure bearing 14, so as to prevent the gas in the high-pressure chamber 13 from being unable to be quickly transported to the throttle 15.

[0044] The cylinder wall of the cylinder 11 is provided with a first air hole connecting the high-pressure chamber 13 and the buffer chamber 113, so that the gas in the high-pressure chamber 13 can enter the buffer chamber 113 through the first air hole. The cylinder wall of the cylinder 11 is also provided with a second air hole 115, which is used to connect the buffer chamber 113 and the air flow channel 114, so that the gas in the buffer chamber 113 can smoothly enter the air flow channel 114.

[0045] Specifically, whether the throttle 15 is in the on state or the off state, the high-pressure gas in the high-pressure chamber 13 can enter the buffer chamber 113 through the first air hole. When the throttle 15 is in the on state, the gas in the buffer chamber 113 can flow to the air flow channel 114 through the second air hole 115, and is transported by the throttle 15 to between the static pressure bearing 14 and the piston 12.

[0046] In some embodiments of the present invention, the cylinder 11 includes a cylinder body 111 and a cylinder head 112. The cylinder body 111 has an opening, and the cylinder head 112 is arranged at the opening of the cylinder body 111. The cylinder body 111 and the cylinder head 112 can be fixedly connected by bolts, rivets, welding and other connection methods.

[0047] In some embodiments, the buffer chamber 113 is disposed on the cylinder body 111, the air flow channel 114 is also disposed on the cylinder body 111, and the first air hole and the second air hole 115 are both provided on the cylinder body 111. The high-pressure gas in the high-pressure chamber 13 enters the buffer chamber 113 in the cylinder wall of the cylinder body 111 through the first air hole, and the gas in the buffer chamber 113 enters the air flow channel 114 in the cylinder wall of the cylinder body 111 through the second air hole 115, and then is transported to the throttle 15. In this embodiment, the gas drawn out from the high-pressure chamber 13 flows in the cylinder wall of the cylinder body 111.

[0048] In some embodiments, the buffer chamber 113 is provided on the cylinder body 111, the air flow channel 114 is provided on the cylinder head 112, the first air hole is provided on the cylinder body 111, and the second air hole 115 is provided on the cylinder head 112. The high-pressure gas in the high-pressure chamber 13 enters the buffer chamber 113 in the cylinder wall of the cylinder body 111 through the first air hole, and the gas in the buffer chamber 113 enters the air flow channel 114 in the cylinder head 112 through the second air hole 115, and then is transported to the throttle 15. In this embodiment, the gas drawn out from the high-pressure chamber 13 flows in the walls of the cylinder body 111 and the cylinder head 112.

[0049] In some embodiments, the buffer chamber 113 is disposed on the cylinder head 112 , the first air hole and the second air hole 115 are both disposed on the cylinder head 112 , the high-pressure chamber 13 is connected to the buffer chamber 113 through the first air hole, and the air flow channel 114 is connected to the buffer chamber 113 through the second air hole 115 .

[0050] Optionally, the air flow channel 114 is disposed in the cylinder body 111, one end of the air flow channel 114 is located at the open end of the cylinder body 111, and the other end of the air flow channel 114 extends to the outer peripheral wall of the static pressure bearing 14 and is connected to the throttle 15. In this way, the high-pressure gas in the high-pressure chamber 13 enters the buffer chamber 113 in the cylinder head 112 through the first air hole, and the gas in the buffer chamber 113 enters the air flow channel 114 in the cylinder wall of the cylinder body 111 through the second air hole 115, and then is transported to the throttle 15. In this embodiment, the gas drawn out from the high-pressure chamber 13 flows in the cylinder head 112 and the cylinder body 111.

[0051] Optionally, the air flow channel 114 is disposed in the cylinder head 112 . In this embodiment, the gas drawn out from the high pressure chamber 13 flows in the cylinder head 112 .

[0052] It should be noted that the buffer chamber 113 is arranged on the cylinder wall of the cylinder body 111, or the air flow channel 114 is arranged on the cylinder wall of the cylinder body 111. It can be understood that the buffer chamber 113 and the air flow channel 114 are cavities formed by the thick part of the wall of the cylinder body 111, or they can be cavities formed by partitions.

[0053] In some embodiments of the present invention, see Figure 2 The buffer chamber 113 is provided on the cylinder head 112, the air flow channel 114 is provided on the cylinder body 111, and the first air hole and the second air hole 115 are opened on the cylinder head 112. The air flow channel 114 is extended along the axial direction of the cylinder body 111, one end of the air flow channel 114 extends to the end of the cylinder body 111 with an opening, and the other end of the air flow channel 114 extends to the vicinity of the static pressure bearing 14. Among them, a connecting hole 117 is provided on the inner wall of the cylinder body 111, one end of the connecting hole 117 is connected to the air flow channel 114, and the other end of the connecting hole 117 penetrates the inner wall of the cylinder body 111 to the outer peripheral wall of the static pressure bearing 14. After the gas in the buffer chamber 113 enters the gas channel through the second air hole 115, it is transported to the static pressure bearing 14 through the connecting hole 117. Through the setting of the connecting hole 117, the air flow channel 114 can extend along the axial direction of the cylinder body 111, which is more convenient for the processing of the air flow channel 114.

[0054] Optionally, the length direction of the communication hole 117 is perpendicular to the direction of the airflow channel 114, the direction of the airflow channel 114 is parallel to the axial direction of the cylinder body 111, and the length direction of the communication hole 117 is parallel to the radial direction of the cylinder body 111. In other embodiments, the length direction of the communication hole 117 may also be arranged at an acute angle to the radial direction of the cylinder body 111.

[0055] In some embodiments of the present invention, the airflow channel 114 is arranged at an angle to the axial direction of the cylinder body 111 , so that an end of the airflow channel 114 away from the end surface of the cylinder body 111 can directly penetrate the inner wall of the cylinder body 111 .

[0056] In some embodiments of the present invention, see Figure 2 , a mounting hole 142 is provided on the hydrostatic bearing 14, and the mounting hole 142 is used to install the throttle 15. The two ends of the mounting hole 142 respectively penetrate the inner circumferential wall and the outer circumferential wall of the hydrostatic bearing 14, so that the two ends of the throttle 15 can be connected with the external channel outside the hydrostatic bearing 14. The hydrostatic bearing 14 is fixed to the inner circumferential wall of the cylinder 11, and there is a first air gap 17 between the inner circumferential wall of the hydrostatic bearing 14 and the piston 12. When the first air gap 17 is filled with gas, it is the above-mentioned gas cushion. The gas outlet end of the throttle 15 is connected to the first air gap 17. When the throttle 15 is in the conducting state, the gas can be introduced into the first air gap 17 to form a gas cushion.

[0057] In some embodiments, the hydrostatic bearing 14 is fixed in the cylinder 11 by means of screws, rivets or other fixing parts, or the hydrostatic bearing 14 is fixed in the cylinder 11 by means of interference fit, welding or other fixing methods.

[0058] In some embodiments, an annular groove 116 is provided on the inner wall of the cylinder 11, and the hydrostatic bearing 14 is fixedly disposed in the annular groove 116. The inner wall of the hydrostatic bearing 14 has the same diameter as the inner wall of the cylinder 11 where the annular groove 116 is not provided. That is, the inner wall of the hydrostatic bearing 14 and the inner wall of the cylinder 11 where the annular groove 116 is not provided form a cylindrical inner wall. During the movement of the piston 12, its outer peripheral wall can move to be adjacent to the inner wall of the hydrostatic bearing 14, or it can move to be adjacent to the inner wall of the cylinder 11.

[0059] In some embodiments, the hydrostatic bearing 14 is fixed to the inner wall of the cylinder 11 , the inner wall diameter of the hydrostatic bearing 14 is smaller than the inner wall diameter of the cylinder 11 , and the piston 12 is always adjacent to the inner wall of the hydrostatic bearing 14 during the movement.

[0060] In some embodiments, the hydrostatic bearing 14 and the cylinder 11 are two components that are manufactured or purchased separately. When the compressor is installed, the hydrostatic bearing 14 and the cylinder 11 are fixedly assembled. Alternatively, the hydrostatic bearing 14 and the cylinder 11 are integrally formed, the hydrostatic bearing 14 is a part of the cylinder 11, and the throttle 15 is also fixedly installed on the cylinder 11 near its inner wall.

[0061] In some embodiments, the inner diameter of the hydrostatic bearing 14 is 23.5 mm±0.003 mm, and the piston 12 is adapted to the size of the hydrostatic bearing 14 .

[0062] In some embodiments of the present invention, an air intake cavity is formed between the outer circumferential wall of the hydrostatic bearing 14 and the inner circumferential wall of the cylinder body 111, one end of the air flow channel 114 is connected to the air intake cavity, and the air intake end of the throttle 15 is also connected to the air intake cavity, so that the air intake end of the throttle 15 has a relatively sufficient air intake space.

[0063] In some embodiments of the present invention, see Figure 2 There is a second air gap between the outer circumferential wall of the hydrostatic bearing 14 and the inner circumferential wall of the cylinder body 111, and the second air gap is connected to the air flow channel 114. The gas enters the second air gap from the air flow channel 114, and then enters the first air gap 17 between the hydrostatic bearing 14 and the piston 12 through the throttle 15. When there are multiple throttles 15, each throttle 15 can be located in the area corresponding to the second air gap, so that the pressure at the inlet end of each throttle 15 is roughly the same, so that the intake and exhaust volumes of each throttle 15 are more uniform. In addition, since the width of the second air gap is narrow, it is more convenient to set a sealing structure 16 at both ends of the second air gap, so that it is easier to seal the gas flow space such as the air flow channel 114, the buffer cavity 113, and the second air gap.

[0064] In some embodiments of the present invention, see Figure 2 At least two sealing structures 16 are arranged between the outer circumferential wall of the hydrostatic bearing 14 and the inner circumferential wall of the cylinder 11. The sealing structures 16 are used to seal the second air gap. The two sealing structures 16 can be arranged at the two axial ends of the second air gap. At the same time, the two sealing structures 16 are respectively located at the two axial ends of the hydrostatic bearing 14, so that the two sealing structures 16, the outer circumferential wall of the hydrostatic bearing 14, and the inner circumferential wall of the cylinder 11 mutually surround the above-mentioned second air gap. The throttle 15 is located between the two sealing structures 16, that is, the throttle 15 is located in the area corresponding to the second air gap, so that the throttle 15 can be connected with the air flow channel 114. By setting the sealing structure 16, the second air gap can be sealed, so that most of the gas derived from the high-pressure chamber 13 can enter between the hydrostatic bearing 14 and the piston 12, avoiding gas leakage.

[0065] Optionally, the outer peripheral wall of the hydrostatic bearing 14 is provided with a first sealing groove 143, the sealing structure 16 is located in the first sealing groove 143, and the sealing structure 16, the inner wall of the first sealing groove 143 and the inner peripheral wall of the cylinder 11 are mutually squeezed to form a seal. Alternatively, the inner peripheral wall of the cylinder 11 is provided with a second sealing groove, and the sealing structure 16, the inner wall of the second sealing groove and the outer peripheral wall of the hydrostatic bearing 14 are mutually squeezed to form a seal. Alternatively, the outer peripheral wall of the hydrostatic bearing 14 is provided with a first sealing groove 143, and the inner peripheral wall of the cylinder 11 is provided with a second sealing groove, and the first sealing groove 143 and the second sealing groove together constitute a sealing groove for accommodating the sealing structure 16, and the sealing structure 16, the inner wall of the first sealing groove 143 and the inner wall of the second sealing groove are mutually squeezed to form a seal.

[0066] Optionally, the sealing structure 16 is a sealing ring, and the cross section of the sealing ring can be a circular, D-shaped, C-shaped or other structure.

[0067] In some embodiments, see Figure 2 The outer peripheral wall of the hydrostatic bearing 14 is concave to form a sink 141, and the inner wall of the sink 141 and the inner peripheral wall of the cylinder body 111 form a second air gap. The mounting holes 142 are all opened on the bottom wall of the sink 141, and the throttle 15 is installed at the sink 141. A height difference is formed between the bottom wall of the sink 141 and the outer peripheral wall of the hydrostatic bearing 14, so that the second air gap can be formed by using the height difference, and the second air gap does not need to be formed by other structural designs, which makes full use of the space in the compression cylinder 1. Among them, the bottom wall of the sink 141 is an inner wall parallel to the outer peripheral wall of the hydrostatic bearing 14.

[0068] Optionally, the thickness of the hydrostatic bearing 14 at the groove 141 is greater than the axial length of the throttle 15. The thickness of the hydrostatic bearing 14 at the groove 141 is the difference between the thickness of the hydrostatic bearing 14 at the groove 141 where the groove 141 is not provided and the depth of the groove 141. The axial length of the throttle 15 is the flow direction of the gas in the throttle 15. When the thickness of the hydrostatic bearing 14 at the groove 141 is greater than the axial length of the throttle 15, both ends of the throttle 15 are located inside the mounting hole 142 and will not extend out, thereby preventing the throttle 15 from moving in its axial position or even protruding from the hydrostatic bearing 14 when the mounting accuracy of the throttle 15 is insufficient.

[0069] Optionally, the depth of the groove 141 is between 1 mm and 2 mm. When the depth of the groove 141 is too large, it will affect the strength of the hydrostatic bearing 14 . When the depth of the groove 141 is too small, the thickness of the second air gap is too small and sufficient hydrostatic pressure cannot be generated on the piston 12 .

[0070] In some embodiments, the inner wall of the cylinder 11 is concave to form a sink 141 , and a second air gap is formed between the inner wall of the sink 141 and the outer wall of the static pressure bearing 14 , and the throttle 15 is arranged opposite to the sink 141 .

[0071] In some embodiments of the present invention, see Figure 3 and Figure 4 A plurality of throttle assemblies are arranged in sequence along the axial direction of the hydrostatic bearing 14. The plurality of throttle assemblies can be arranged at equal intervals along the axial direction of the hydrostatic bearing 14, which facilitates the processing of the hydrostatic bearing 14 and makes the intake speed of each part of the second air gap between the hydrostatic bearing 14 and the piston 12 more uniform.

[0072] The throttle assembly includes at least one throttle 15. When the throttle assembly includes multiple throttles 15, the multiple throttles 15 are distributed along the circumference of the static pressure bearing 14, so that each circumferential part of the second air gap can be filled with air, so that the circumferential static pressure generated by the gas in the second air gap is more uniform. The number of throttle assemblies and the number of throttles 15 in each throttle assembly are not limited here, and can be determined according to the specific analysis of the force on the piston 12. Figure 3 and Figure 4 In the embodiment, the number of throttle assemblies is 4, and the number of throttles 15 in each throttle assembly is 6.

[0073] In some embodiments of the present invention, a throttle assembly is disposed on the hydrostatic bearing 14 , and the throttle assembly includes at least one throttle 15 .

[0074] In some embodiments of the present invention, see Figure 5 The throttle 15 has a throttle hole 150 arranged along its axial direction. After the gas passes through the throttle hole 150, the high-pressure gas can be reduced to a low-pressure gas. One end of the throttle hole 150 is the air inlet end, and the other end is the air outlet end. The throttle hole 150 includes an air inlet section 151, a neck section 152 and an air outlet section 153 connected in sequence. The end of the air inlet section 151 away from the neck section 152 is the air inlet end of the throttle hole 150, and the end of the air outlet section 153 away from the neck section 152 is the air outlet end of the throttle hole 150. The aperture of the neck section 152 is smaller than the aperture of the air inlet section 151 and smaller than the aperture of the air outlet section 153. The small aperture of the neck section 152 can prevent the gas with a higher pressure from entering the air inlet section 151 from the air outlet section 153. The gas outlet section 153 is arranged in a conical shape, and the end of the gas outlet section 153 with a smaller aperture is connected to the neck section 152, so that the aperture of the gas outlet section 153 facing the second air gap is larger, and the gas can be guided into the second air gap more quickly.

[0075] Optionally, the cone angle of the air outlet section 153 ranges from 90° to 120°, such as 90°, 100°, 115°, etc. When the cone angle is too large, the strength of the throttle 15 is easily reduced. When the cone angle is too small, the fluid resistance of the gas from the neck section 152 of the throttle 15 to the second air gap is too large, and the airflow flows slowly, which affects the stability of the gas cushion.

[0076] See also Figure 1 The present invention further provides a compressor, which includes the compression cylinder 1 in any of the above embodiments. The compressor also includes a motor 2, a crankshaft 3 and other structures. When the motor 2 is working, it drives the crankshaft 3 to rotate. The rotation of the crankshaft 3 causes the piston 12 to reciprocate inside the cylinder 11, thereby compressing the gas.

[0077] The compressor provided by the present invention adopts the above-mentioned compression cylinder 1, a high-pressure chamber 13 is formed between the cylinder 11 and the piston 12 of the compression cylinder 1, a hydrostatic bearing 14 is arranged at the inner wall of the cylinder 11, and a throttle 15 is arranged on the hydrostatic bearing 14. An air flow channel 114 is arranged in the cylinder wall of the cylinder 11, and the high-pressure chamber 13, the air flow channel 114 and the throttle 15 are connected in sequence, so that the high-pressure gas in the high-pressure chamber 13 can be transported to the throttle 15 through the air flow channel 114, and the throttle 15 reduces the pressure of the high-pressure gas and transports it to between the hydrostatic bearing 14 and the piston 12, so that an air gap layer is formed between the hydrostatic bearing 14 and the piston 12, and the piston 12 is supported by the air gap layer to prevent the piston 12 and the cylinder 11 from colliding with each other, thereby reducing the wear of the surface of the piston 12 and the inner wall of the cylinder 11, and improving the compression efficiency of the compressor.

[0078] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions and improvements made within the spirit and principles of the present invention should be included in the protection scope of the present invention.

Claims

1. A compression cylinder, comprising a cylinder and a piston disposed in the cylinder, wherein the piston can move relative to the cylinder, and wherein the cylinder has a high-pressure chamber for compressing gas. Features: A hydrostatic bearing for supporting the piston is arranged on the inner wall of the cylinder, a first air gap is provided between the inner peripheral wall of the hydrostatic bearing and the outer peripheral wall of the piston, a throttle is provided on the hydrostatic bearing, an air flow channel connected to the high-pressure chamber is provided in the cylinder wall of the cylinder, and the high-pressure chamber, the air flow channel, the throttle and the first air gap are connected in sequence.

2. The compression cylinder according to claim 1, Features: The cylinder wall of the cylinder also has a buffer chamber, and the high-pressure chamber, the buffer chamber and the air flow channel are connected in sequence.

3. The compression cylinder according to claim 2, Features: The cylinder includes a cylinder body with an opening and a cylinder cover arranged at the opening, the cylinder cover is provided with a first air hole and a second air hole, and the buffer chamber is arranged in the cylinder cover, the high-pressure chamber is connected with the buffer chamber through the first air hole, and the air flow channel is connected with the buffer chamber through the second air hole.

4. The compression cylinder according to claim 3, Features: The cylinder body has the air flow passage, one end of which is located at the end of the cylinder body having the opening, and the other end of which extends to the outer peripheral wall of the static pressure bearing and is communicated with the throttle.

5. The compression cylinder according to claim 4, Features: The air flow channel is extended along the axial direction of the cylinder body, and a connecting hole is provided on the inner wall of the cylinder body. One end of the connecting hole is connected to the air flow channel, and the other end of the connecting hole passes through the inner wall of the cylinder body to the outer peripheral wall of the static pressure bearing.

6. The compression cylinder according to any one of claims 1 to 5, Features: The hydrostatic bearing is fixed to the inner wall of the cylinder, and has mounting holes at both ends respectively penetrating the inner circumferential wall and the outer circumferential wall thereof, the throttle is fixed in the mounting hole, and a second air gap is provided between the outer circumferential wall of the hydrostatic bearing and the inner circumferential wall of the cylinder body, and the second air gap is connected to the air flow channel.

7. The compression cylinder according to claim 6, Features: At least two sealing structures are arranged between the outer circumferential wall of the hydrostatic bearing and the inner circumferential wall of the cylinder, wherein the two sealing structures are respectively located at the axial ends of the hydrostatic bearing, so that the two sealing structures seal the axial ends of the second air gap, and the throttle is located between the two sealing structures.

8. The compression cylinder according to claim 6, Features: The outer peripheral wall of the static pressure bearing is concave to form a sink groove, the inner wall of the sink groove and the inner peripheral wall of the cylinder body form the second air gap, and the mounting holes are all opened on the bottom wall of the sink groove.

9. The compression cylinder according to claim 8, Features: The thickness of the static pressure bearing at the sink groove is greater than the axial length of the throttle.

10. The compression cylinder according to any one of claims 1 to 5, Features: A plurality of throttle assemblies are sequentially and spaced apart along the axial direction of the hydrostatic bearing, and the throttle assembly includes a plurality of throttles distributed along the circumference of the hydrostatic bearing.

11. The compression cylinder according to any one of claims 1 to 5, Features: The throttle has a throttling hole arranged along its axial direction, and the throttling hole includes an air inlet section, a neck section and an air outlet section connected in sequence. The air outlet section is arranged in a conical shape, and the aperture of the neck section is smaller than the aperture of the air inlet section and smaller than the aperture of the air outlet section.

12. The compression cylinder according to claim 11, Features: The cone angle of the air outlet section ranges from 90° to 120°.

13. Compressor, Features: Comprising the compression cylinder according to any one of claims 1-12.

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