Portable horizontally-opposed oil-free four-cylinder compressor and oxygen production equipment

Abstract

The embodiment of the invention provides a portable horizontally-opposed oil-free four-cylinder compressor and oxygen production equipment, and relates to the technical field of medical instruments. The compressor comprises a motor and two sets of air cylinder assemblies, the motor comprises two output shafts, and the two output shafts are arranged on the two sides of the motor correspondingly; the two output shafts are each provided with an air cylinder assembly. The cylinder assembly comprises a first eccentric crankshaft, a second eccentric crankshaft, a first cylinder and a second cylinder. The first eccentric crankshaft is connected to the output shaft, and a first connecting part is arranged on the side, away from the motor, of the first eccentric crankshaft. The second eccentric crankshaft is connected to the first connecting part, and a second connecting part is arranged on the side, away from the first eccentric crankshaft, of the second eccentric crankshaft. The central axis of the output shaft, the central axis of the first connecting part and the central axis of the second connecting part are not collinear. According to the compressor provided by the embodiment of the invention, the application of vacuum pressure swing adsorption in a portable oxygen generator can be realized.

Description

Technical Field

[0001] This application relates to the field of medical device technology, and in particular to a portable horizontally opposed oil-free four-cylinder compressor and oxygen generator. Background Technology

[0002] Oxygen, an essential substance for human life, has significant applications in medical emergency care, high-altitude hypoxic environments, treatment of chronic respiratory diseases, and rehabilitation and healthcare. With advancements in medical technology and increasing demand for portable devices, oxygen concentrators have gradually expanded from traditional centralized hospital oxygen supply systems to home and portable applications.

[0003] Currently, oxygen generators are based on the molecular sieve physical adsorption method. By utilizing the selective adsorption characteristics of molecular sieves for nitrogen in the air, nitrogen and oxygen are separated, thereby extracting high-purity oxygen. In the structure of the oxygen generator, the compressor, as the core component of the entire oxygen generation system, plays the role of providing a stable pressure source for the molecular sieve adsorption and desorption processes. Its performance parameters, size, and weight directly determine the overall performance and portability of the oxygen generator.

[0004] In related technologies, oxygen concentrators typically use PSA dual-cylinder compressors to meet the requirement of small device size. Medical oxygen concentrators usually use VPSA multi-cylinder compressors to meet the power and flow requirements in the oxygen generation process. However, current VPSA multi-cylinder compressors are relatively large, making it difficult to meet the requirements of small device size and portability. Summary of the Invention

[0005] This application provides a portable horizontally opposed oil-free four-cylinder compressor and oxygen generator, reducing the size of the compressor and thus the size of the oxygen generator to meet the requirements of small size and portability of the oxygen generator.

[0006] In a first aspect, embodiments of this application provide a portable horizontally opposed oil-free four-cylinder compressor, comprising:

[0007] The motor and two sets of cylinder assemblies are included. The motor includes two output shafts, which are respectively located on both sides of the motor and are coaxially aligned. A cylinder assembly is mounted on each of the two output shafts. The cylinder assembly includes:

[0008] A first eccentric crankshaft is connected to the output shaft, and a first connecting part is provided on the side of the first eccentric crankshaft away from the motor;

[0009] The second eccentric crankshaft is connected to the first connecting part, and the second connecting part is provided on the side of the second eccentric crankshaft away from the first eccentric crankshaft;

[0010] The first cylinder includes a first cylinder body and a first piston member. The first piston member includes a first piston head and a first rotating part. The first rotating part is located between a first eccentric crankshaft and a second eccentric crankshaft and is rotatably connected to a first connecting part.

[0011] The second cylinder includes a second cylinder body and a second piston component. The second piston component includes a second rotating part and a second piston head. The second rotating part is rotatably connected to the second connecting part.

[0012] The central axis of the output shaft, the central axis of the first connecting part, and the central axis of the second connecting part are not collinear.

[0013] In some embodiments, the first connecting portion and the second connecting portion are arranged at a 180° phase with respect to the output shaft, and the central axis of the first connecting portion and the central axis of the second connecting portion are parallel to the central axis of the output shaft.

[0014] In some embodiments, one of the two cylinder assemblies is defined as the first cylinder assembly and the other as the second cylinder assembly;

[0015] The first connecting portion in the first cylinder assembly and the first connecting portion in the second cylinder assembly are arranged at a 180° phase relative to the central axis of the output shaft, so that the first piston in the first cylinder assembly moves in opposite directions to the first piston in the second cylinder assembly.

[0016] In some embodiments, the first eccentric crankshaft includes a first mounting hole connected to the output shaft; the second eccentric crankshaft includes a second mounting hole connected to the first connecting portion.

[0017] The distance between the center of the first mounting hole and the central axis of the first connecting part is the first eccentric distance, and the distance between the center of the second mounting hole and the central axis of the second connecting part is the second eccentric distance. Both the first eccentric distance and the second eccentric distance are 2.9~3.6mm.

[0018] In some embodiments, the first eccentric crankshaft includes a first counterweight, which is located on the side of the first mounting hole away from the first connection portion.

[0019] The second eccentric crankshaft includes a second counterweight, which is located on the side of the second mounting hole away from the second connection part.

[0020] The outer contours of the first counterweight and the second counterweight are arc-shaped, and the radius of the outer contour of the first counterweight is less than or equal to the radius of the outer contour of the first rotating part, and the radius of the outer contour of the second counterweight is equal to the radius of the outer contour of the second rotating part.

[0021] In some embodiments, the first cylinder further includes a first valve plate, and the second cylinder further includes a second valve plate;

[0022] At least one of the first valve plate and the first piston head has a first clearance portion on the opposite side;

[0023] And / or, at least one of the second valve plate and the second piston head has a second clearance portion on the opposite side.

[0024] In some embodiments, the first clearance portion and / or the second clearance portion is a clearance ramp or a clearance groove.

[0025] In some embodiments, the compressor further includes:

[0026] The intake pipe includes a first intake pipe and a second intake pipe. Both the first and second intake pipes are used to receive airflow. The intake ports of the two first cylinders are connected through the first intake pipe, and the intake ports of the two second cylinders are connected through the second intake pipe.

[0027] The exhaust pipe is used to discharge airflow. The exhaust pipe includes a first exhaust pipe and a second exhaust pipe. Both the first exhaust pipe and the second exhaust pipe are used to discharge airflow. The exhaust ports of the two first cylinders are connected through the first exhaust pipe, and the exhaust ports of the two second cylinders are connected through the second exhaust pipe.

[0028] In some embodiments, the compressor further includes a muffler housing, which is mounted on the outer surface of the motor in the compressor, and the muffler housing is provided with an intake passage and an exhaust passage.

[0029] The air intake end of the air intake channel is used to communicate with the outside of the muffler housing, and the air outlet end of the air intake channel is connected to the first air intake pipe;

[0030] The exhaust outlet of the exhaust passage is used to connect with the outside of the muffler housing, and the intake end of the exhaust passage is connected with the exhaust port of the second exhaust pipe.

[0031] In some embodiments, multiple partitions are provided in both the intake and exhaust channels, dividing the intake and exhaust channels into multiple chambers to form multi-stage noise reduction; noise reduction through holes are provided on the partitions.

[0032] In some embodiments, the muffler housing has a mounting cavity whose shape matches the shape of the circumferential outer wall of the motor; the mounting cavity surrounds at least a portion of the motor.

[0033] Secondly, embodiments of this application also provide an oxygen generating device, including the portable horizontally opposed oil-free four-cylinder compressor in any of the above embodiments.

[0034] This application provides a portable horizontally opposed oil-free four-cylinder compressor and an oxygen generator. The compressor connects a first eccentric crankshaft to an output shaft, a second eccentric crankshaft to a first eccentric crankshaft, a first rotating part of a first piston to a first connecting part, and a second rotating part of a second piston to a second connecting part, so that the first rotating part will move in a circular motion around the central axis of the first connecting part, and the second rotating part will move in a circular motion around the central axis of the second connecting part.

[0035] In this way, the first rotating part does not need to be fitted onto the outer contour of the first eccentric crankshaft, and the second rotating part does not need to be fitted onto the outer contour of the second eccentric crankshaft. Therefore, there is no need to set a large-diameter eccentric bearing, which allows the outer contour dimensions of the first rotating part and the second rotating part to be reduced in the radial direction of the output shaft. This reduces the space occupied by the first and second rotating parts when they rotate, and also reduces the overall space occupied by the first and second piston components. This improves the compactness of the internal structure of the four-cylinder compressor and helps to reduce the overall size and weight of the four-cylinder compressor, so that the four-cylinder compressor can be integrated into small portable oxygen generators with higher space requirements.

[0036] Meanwhile, in this embodiment, the output shaft is only rotatedly connected to the first eccentric crankshaft, so that the output shaft does not pass through the second eccentric crankshaft, which helps to reduce the length of the output shaft and also reduces the space occupied by the power transmission components.

[0037] Furthermore, since the compressor in this embodiment has two coaxially arranged output shafts, under the drive of the motor, the output shafts on both sides can synchronously drive the cylinder assemblies on both sides to operate, thereby giving the four-cylinder compressor a larger displacement and power, thus meeting the flow and power requirements of the oxygen generating equipment. Attached Figure Description

[0038] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0039] Figure 1 This is a schematic diagram of the compressor provided in an embodiment of this application;

[0040] Figure 2 A schematic diagram of the unfolded structure of the compressor provided in an embodiment of this application;

[0041] Figure 3 A cross-sectional schematic diagram of the compressor provided in an embodiment of this application;

[0042] Figure 4 A schematic diagram of the installation of the first piston and the second piston of the compressor provided in the embodiments of this application;

[0043] Figure 5 This is a schematic diagram of the output end of the compressor provided in an embodiment of this application;

[0044] Figure 6 for Figure 5 A schematic diagram of the unfolded structure of the output end of the motor;

[0045] Figure 7 for Figure 5 Cross-sectional schematic diagram of the output end structure of the motor;

[0046] Figure 8 A cross-sectional schematic diagram of the connection structure between the motor and the first eccentric crankshaft and the second eccentric crankshaft provided in the embodiments of this application;

[0047] Figure 9 This is a schematic diagram of the structure of the first eccentric crankshaft of the compressor provided in an embodiment of this application;

[0048] Figure 10 This is a schematic diagram of the structure of the second eccentric crankshaft of the compressor provided in an embodiment of this application;

[0049] Figure 11 A schematic diagram of the rotation trajectory of the cylinder assembly provided in the embodiments of this application;

[0050] Figure 12 A schematic diagram showing the unfolded structure of the compressor's intake pipe and exhaust pipe provided in the embodiments of this application;

[0051] Figure 13 This is a schematic diagram of the structure of the compressor's silencer housing provided in an embodiment of this application;

[0052] Figure 14 A first unfolded schematic diagram of the compressor's silencer housing provided in an embodiment of this application;

[0053] Figure 15 This is a second unfolded schematic diagram of the silencer housing of the compressor provided in an embodiment of this application;

[0054] Figure 16 This is a schematic diagram of the internal structure of the compressor's silencer housing provided in an embodiment of this application;

[0055] Figure 17 This is a schematic cross-sectional view of the first cylinder body of the first cylinder of the compressor provided in an embodiment of this application.

[0056] Figure 18 A schematic diagram of the structure of the first valve plate of the first cylinder of the compressor provided in the embodiments of this application;

[0057] Figure 19 This is a schematic cross-sectional view of the second cylinder body of the compressor provided in an embodiment of this application.

[0058] Figure 20 This is a schematic diagram of the structure of the second valve plate of the second cylinder of the compressor provided in an embodiment of this application;

[0059] Figure 21 A cross-sectional structural schematic diagram of the first cylinder provided in an embodiment of this application;

[0060] Figure 22 This is a schematic diagram of the structure of the first piston component provided in an embodiment of this application;

[0061] Figure 23 A cross-sectional structural schematic diagram of the second cylinder provided in an embodiment of this application;

[0062] Figure 24 This is a schematic diagram of the structure of the second piston component provided in an embodiment of this application;

[0063] Figure 25 A front view of the first piston component provided in an embodiment of this application;

[0064] Figure 26 A front view of the second piston provided in an embodiment of this application.

[0065] Figure label:

[0066] 100 - Motor; 110 - Output shaft;

[0067] 200 - Cylinder assembly; 210 - First eccentric crankshaft; 211 - First connecting part; 212 - First counterweight part; 213 - First mounting hole; 220 - Second eccentric crankshaft; 221 - Second connecting part; 222 - Second counterweight part; 223 - Second mounting hole;

[0068] 230 - First cylinder; 231 - First piston; 232 - First cylinder body; 233 - First valve plate; 234 - First clearance groove; 235 - First piston head; 236 - First clearance slope; 237 - First rotating part;

[0069] 240 - Second cylinder; 241 - Second piston; 242 - Second cylinder body; 243 - Second valve plate; 244 - Second clearance groove; 245 - Second piston head; 246 - Second clearance slope; 247 - Second rotating part;

[0070] 300 - Intake pipe; 310 - First intake pipe; 320 - Second intake pipe; 330 - First main pipe section; 340 - First branch pipe section;

[0071] 400 - Exhaust pipe; 410 - First exhaust pipe; 420 - Second exhaust pipe; 430 - Second main pipe section; 440 - Second branch pipe section;

[0072] 500 - Silencing housing; 510 - Air intake passage; 520 - Exhaust passage; 530 - Partition plate; 531 - Noise reduction through hole; 540 - Mounting cavity. Detailed Implementation

[0073] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0074] The embodiments or implementation methods in this application are described in a progressive manner. Each embodiment focuses on the differences from other embodiments, and the same or similar parts between the embodiments can be referred to each other.

[0075] It should be noted that, in the description of this application, the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0076] This application provides an oxygen generating device. The oxygen generating device can be a home oxygen concentrator, a car oxygen concentrator, an outdoor emergency oxygen generating device, or any other device capable of producing oxygen. The oxygen generating device is suitable for scenarios such as medical emergency care, chronic disease management (e.g., home treatment for COPD patients), altitude sickness relief, and outdoor emergency situations.

[0077] Oxygen generators use physical adsorption technology to separate nitrogen from the air and extract high-purity oxygen. The compressors in oxygen generators include pressure swing adsorption compressors (PSA compressors) and vacuum pressure swing adsorption compressors (VPSA multi-cylinder compressors). PSA compressors are typically dual-cylinder compressors, and their smaller size meets the volume requirements of household and portable oxygen generators.

[0078] Vacuum pressure swing adsorption compressors can provide more power output and more stable flow supply, making them suitable for medical and other scenarios with high requirements for oxygen production power and gas flow, and meeting the pressure and flow requirements in the medical oxygen production process.

[0079] With advancements in medical technology and increasing demand for portable devices, oxygen concentrators have gradually expanded from traditional centralized hospital oxygen supply systems to home and portable applications. However, current vacuum pressure swing adsorption compressors are mostly four- or eight-cylinder structures, which are relatively large and do not easily meet the size requirements of home and portable oxygen concentrators.

[0080] Currently, most mainstream VPSA compressors are four-cylinder or eight-cylinder structures. The motor output shaft of the compressor passes directly through an eccentric bearing or eccentric crankshaft. The eccentricity converts the circular motion of the motor into the reciprocating motion of the piston, thereby realizing the compression and intake actions of the cylinder.

[0081] Because the motor output shaft needs to pass directly through the eccentric crankshaft, a through hole matching the through shaft must be reserved on the eccentric crankshaft. The setting of this through hole occupies the internal space of the eccentric crankshaft, making it impossible to further reduce the structural size of the eccentric crankshaft. Secondly, in order to realize the conversion of the motor's circular motion into the piston's reciprocating motion, the eccentric crankshaft must have a certain eccentricity. The existence of eccentricity requires the diameter of the eccentric crankshaft to be increased accordingly, which in turn increases the overall outer contour size of the eccentric crankshaft.

[0082] Furthermore, the piston is typically rotatably mounted on the outer contour of an eccentric crankshaft. Due to the increased overall size of the eccentric crankshaft, the rotational space at the connection point between the piston and the crankshaft increases as the piston rotates with it. Consequently, the piston-crankshaft transmission structure occupies a significant amount of internal space in the VPSA compressor, making it difficult to control the overall size of the compressor. This hinders its ability to meet the miniaturization requirements of portable medical oxygen generators and increases the overall weight of the compressor, reducing portability and failing to meet the current demands for miniaturization, portability, high efficiency, and stability in medical oxygen generators.

[0083] Based on this, this application provides a portable horizontally opposed oil-free four-cylinder compressor, which aims to solve the above-mentioned technical problems.

[0084] The technical solution of this application and how the technical solution of this application solves the above-mentioned technical problems are described in detail below with specific embodiments. These specific embodiments can be combined with each other, and the same or similar concepts or processes may not be described again in some embodiments. The embodiments of this application will now be described with reference to the accompanying drawings.

[0085] Firstly, please refer to Figures 1 to 3This application provides a portable horizontally opposed oil-free four-cylinder compressor, which includes a motor 100 and two sets of cylinder assemblies 200.

[0086] The motor 100 includes two output shafts 110, which are respectively disposed on both sides of the motor 100 and are coaxially arranged. A set of cylinder assemblies 200 is mounted on each of the two output shafts 110, and can provide synchronous and stable power support for the two sets of cylinder assemblies 200.

[0087] See Figure 1 and Figure 3 The motor 100 has a left and a right side opposite each other in the X direction. One of the two output shafts 110 is located on the left side of the motor 100, and the other is located on the right side of the motor 100. Correspondingly, one set of two sets of cylinder assemblies 200 is located on the left side of the motor 100, and the other set is located on the right side of the motor 100.

[0088] Since the two output shafts 110 are coaxially arranged, when the motor 100 is running, the two sets of cylinder assemblies 200 can run synchronously with the two output shafts 110.

[0089] The structure of cylinder assembly 200 is described in detail below.

[0090] Please see Figures 4 to 8 The cylinder assembly 200 serves as the actuator of the compressor to perform gas compression. A single cylinder assembly 200 includes two eccentric crankshafts and two cylinders. The two eccentric crankshafts are a first eccentric crankshaft 210 and a second eccentric crankshaft 220, and the two cylinders are a first cylinder 230 and a second cylinder 240.

[0091] See Figure 1 and Figure 3 The motor 100 has an upper and a lower side in the Y direction. The first cylinder 230 can be located on the upper side of the motor 100, and the second cylinder 240 can be located on the lower side of the motor 100.

[0092] It should be noted that the two sets of cylinder assemblies 200 in this embodiment can have roughly the same structure; that is, the cylinder assembly 200 on the left side of the motor 100 and the cylinder assembly 200 on the right side of the motor 100 can have essentially the same structure. The first cylinder 230 of both the left and right cylinder assemblies 200 can be located on the upper side of the motor 100, and the second cylinder 240 of both the left and right cylinder assemblies 200 can be located on the lower side of the motor 100.

[0093] The first eccentric crankshaft 210 is used to drive the first piston 231 to move and to drive the second eccentric crankshaft 220 to rotate. The first eccentric crankshaft 210 is fixedly connected to the output shaft 110. The first eccentric crankshaft 210 has a first connecting part 211 on the side away from the motor 100, and the second eccentric crankshaft 220 is fixedly connected to the first connecting part 211.

[0094] Thus, driven by the output shaft 110 of the motor 100, the output shaft 110 can transmit the rotational torque to the first eccentric crankshaft 210, enabling the first eccentric crankshaft 210 to achieve eccentric rotational motion, while the first eccentric crankshaft 210 can drive the second eccentric crankshaft 220 to rotate.

[0095] The second eccentric crankshaft 220 drives the second piston 241 to move. A second connecting portion 221 is provided on the side of the second eccentric crankshaft 220 away from the first eccentric crankshaft 210. The first cylinder 230 includes a first cylinder body 232 and a first piston 231. The first piston 231 includes a first piston head 235 and a first rotating portion 237. The first piston head 235 is movably disposed within the first cylinder body 232. The first rotating portion 237 is located between the first eccentric crankshaft 210 and the second eccentric crankshaft 220 and is rotatably connected to the first connecting portion 211. Because the first connecting portion 211 can follow the eccentric rotational movement of the first eccentric crankshaft 210, the first piston 231 can reciprocate within the first cylinder body 232 via the first rotating portion 237, thereby enabling the first cylinder 230 to perform both gas suction and gas compression.

[0096] The second cylinder 240 includes a second cylinder body 242 and a second piston member 241. The second piston member 241 has a second rotating part 247 and a second piston head 245. The second piston head 245 is movably disposed within the second cylinder body 242, and the second rotating part 247 is rotatably connected to the second connecting part 221. Similarly, since the second connecting part 221 can follow the eccentric rotational movement of the second eccentric crankshaft 220, the second piston member 241 can reciprocate within the second cylinder body 242 via the second rotating part 247, thereby enabling the second cylinder 240 to perform gas suction and gas compression. In this way, the first piston member 231 and the second piston member 241 can work together to complete the gas suction and compression operations.

[0097] The first cylinder 232 and the second cylinder 242 can be cylindrical cavity structures. Both the first cylinder 232 and the second cylinder 242 are provided with air inlets and exhaust ports, and one-way valves can be installed at both the air inlets and exhaust ports to control the unidirectional flow of gas.

[0098] Since the first piston 231 rotates with the first eccentric crankshaft 210, the first rotating part 237 rotates relative to the axis of the output shaft 110, while the first piston head 235 is restricted to slide within the first cylinder 232. This allows the first piston 231 as a whole to slide and oscillate relative to the first cylinder 232. Similarly, the second piston 241 can also slide and oscillate relative to the second cylinder 242.

[0099] Please see Figure 7 and Figure 8 , Figure 7 and Figure 8 The dashed lines in the figure represent the central axes of the output shaft 110, the first connecting part 211, and the second connecting part 221, respectively. In this embodiment, the central axes of the output shaft 110, the first connecting part 211, and the second connecting part 221 of the motor 100 are not collinear, so that the first connecting part 211 and the second connecting part 221 can be distributed on different radial sides of the output shaft 110.

[0100] Therefore, in the compressor provided in this application embodiment, the first eccentric crankshaft 210 is connected to the output shaft 110, the second eccentric crankshaft 220 is connected to the first eccentric crankshaft 210, the first rotating part 237 of the first piston member 231 is connected to the first connecting part 211, and the second rotating part 247 of the second piston member 241 is connected to the second connecting part 221, so that the first rotating part 237 will move in a circular motion around the central axis of the first connecting part 211, and the second rotating part 247 will move in a circular motion around the central axis of the second connecting part 221. In this way, the first rotating part 237 does not need to be fitted onto the outer contour of the first eccentric crankshaft 210, and the second rotating part 247 does not need to be fitted onto the outer contour of the second eccentric crankshaft 220. This eliminates the need for a large-diameter eccentric bearing and reduces the outer contour volume of both the first rotating part 237 and the second rotating part 247. Consequently, it reduces the space occupied by the first rotating part 237 and the second rotating part 247 during rotation and decreases the overall space occupied by the first piston 231 and the second piston 241. This improves the compactness of the compressor's internal structure and helps reduce the overall size and weight of the compressor, allowing it to be integrated into smaller, portable oxygen generators with higher space requirements.

[0101] Meanwhile, in this embodiment, the output shaft 110 is only rotatably connected to the first eccentric crankshaft 210, so that the output shaft 110 passes through the second eccentric crankshaft 220, which helps to reduce the length of the output shaft 110 and also reduces the space occupied by the power transmission components.

[0102] Furthermore, since the compressor in this embodiment has two coaxially arranged output shafts 110, under the drive of the motor 100, the two output shafts 110 can synchronously drive the cylinder assemblies 200 on both sides to operate, thereby enabling the compressor to have a larger displacement and power, thus meeting the flow and power requirements of the oxygen generating equipment.

[0103] In summary, the compressor provided in this embodiment can provide greater flow and power to the oxygen generating equipment while reducing the overall size of the equipment, thereby helping to adapt to the miniaturization requirements of portable medical oxygen generating equipment and meeting the usage needs of multiple scenarios such as high-altitude emergency rescue and outdoor medical treatment.

[0104] The working principle of the compressor in this embodiment is as follows:

[0105] Please see Figure 3 When the motor 100 starts running, the two output shafts 110 on both sides of the motor 100 will rotate synchronously in the same direction. The output shafts 110 will drive the first eccentric crankshaft 210 fixedly connected to them to rotate synchronously. The first eccentric crankshaft 210 transmits the circular motion of the output shaft 110 to the first connecting part 211. Since the central axis of the output shaft 110 is not collinear with the central axis of the first connecting part 211, the first connecting part 211 will rotate around the central axis of the output shaft 110 as the first eccentric crankshaft 210 rotates. At this time, the first rotating part 237 of the first piston 231 will be driven by the first connecting part 211 to perform synchronous circular motion, and the circular motion of the first rotating part 237 will be converted into the reciprocating linear motion of the first piston head 235.

[0106] When the first connecting part 211 rotates to the side away from the first cylinder 232, the first rotating part 237 drives the first piston head 235 to move closer to the output shaft 110 inside the first cylinder 232, thereby creating a negative pressure inside the first cylinder 232 and completing the air intake action; when the first connecting part 211 rotates to the side closer to the first cylinder 232, the first rotating part 237 drives the first piston head 235 to move away from the output shaft 110, thereby compressing the air inside the first cylinder 232, increasing the air pressure inside the first cylinder 232, and completing the compression action.

[0107] Simultaneously, the rotation of the first eccentric crankshaft 210 drives the second eccentric crankshaft 220 to rotate synchronously through the first connecting part 211, and the second eccentric crankshaft 220 can transmit power to the second connecting part 221. Since the central axis of the second connecting part 221 is not collinear with the central axes of the first connecting part 211 and the output shaft 110, the second connecting part 221 will perform circular motion around the central axis of the first connecting part 211, thereby driving the second rotating part 247 of the second piston 241, which is rotatably connected to it, to move synchronously. Consistent with the motion principle of the first piston 231, the circular motion of the second rotating part 247 is converted into the reciprocating linear motion of the second piston head 245 in the second cylinder 242, forming a coordinated action with the first cylinder 230 to complete the air compression and negative pressure nitrogen removal (desorption) actions respectively, jointly supporting the stable operation of the oxygen generation system.

[0108] In the context of the oxygen generator, the first cylinder 230 in this embodiment can compress air and can be used as a positive pressure cylinder. The second cylinder 240 in this embodiment can reduce the pressure of the nitrogen remaining in the molecular sieve to below atmospheric pressure to achieve negative pressure nitrogen removal and can be used as a negative pressure cylinder.

[0109] On the one hand, after the air from the outside environment is drawn into the first cylinder 232, the air is compressed to form high-pressure air. The high-pressure air can be introduced into the molecular sieve device through the exhaust pipe 400. The molecular sieve device can use its adsorption properties to adsorb nitrogen in the high-pressure air, thereby achieving nitrogen-oxygen separation. The separated oxygen is collected through a special oxygen collection pipeline for subsequent oxygen demand.

[0110] On the other hand, after the oxygen is collected in the molecular sieve device, the remaining nitrogen is drawn into the second cylinder 242 through the pipeline and released into the atmosphere.

[0111] Therefore, the compressor in this embodiment, through the coordinated action of the first cylinder 230 and the second cylinder 240 in the cylinder assembly 200, can work with the molecular sieve to realize the adsorption and desorption process, providing the high-pressure air required for nitrogen-oxygen separation and achieving negative pressure nitrogen discharge for the remaining nitrogen, thus ensuring the smooth and efficient oxygen production process.

[0112] Please continue reading. Figures 3 to 8 The mounting structure of cylinder assembly 200 will be further illustrated below with examples.

[0113] The first connecting part 211 can be integrally formed on the side of the first eccentric crankshaft 210 away from the motor 100, and has a cylindrical structure. The central axis of the first connecting part 211 is not collinear with the rotation center axis of the first eccentric crankshaft 210 (i.e., it forms an eccentric setting).

[0114] The first eccentric crankshaft 210 includes a first mounting hole 213, which is fixedly connected to the output shaft 110, enabling the first eccentric crankshaft 210 to rotate synchronously with the output shaft 110, thereby driving the first connecting part 211 of the first eccentric crankshaft 210 to perform eccentric rotational motion. The diameter of the first mounting hole 213 can be adapted to the shaft diameter of the output shaft 110. During assembly, the output shaft 110 of the motor 100 is inserted into the first mounting hole 213. The first mounting hole 213 and the output shaft 110 can be circumferentially fixed through a keyed joint structure or a set screw snap-fit ​​structure.

[0115] For example, the first eccentric crankshaft 210 has a threaded hole on the radial side of the first mounting hole 213. The set screw is screwed into the threaded hole and presses against the outer periphery of the output shaft 110, thereby limiting the radial displacement of the first eccentric crankshaft 210.

[0116] The structure of the second eccentric crankshaft 220 can be adapted to the first eccentric crankshaft 210. The second eccentric crankshaft 220 is provided with a second mounting hole 223 adapted to the first connecting part 211. The first connecting part 211 is fixedly connected to the second mounting hole 223, so that the first eccentric crankshaft 210 can transmit rotational torque through the first connecting part 211, thereby driving the second eccentric crankshaft 220 to rotate synchronously. The second connecting part 221 can be integrally formed on the side of the second eccentric crankshaft 220 away from the first eccentric crankshaft 210, and its structure is the same as that of the first connecting part 211, which is also a cylindrical structure. The central axis of the second connecting part 221 is not collinear with the rotational central axis of the second eccentric crankshaft 220, and is also not collinear with the central axis of the first connecting part 211 or the central axis of the output shaft 110 of the motor 100.

[0117] The first eccentric crankshaft 210 can also have a threaded hole on the radial side of the second mounting hole 223. The set screw is screwed into the threaded hole and presses against the outer periphery of the first connecting part 211, thereby limiting the radial displacement of the second eccentric crankshaft 220.

[0118] The first rotating part 237 is the connection point between the first piston 231 and the first connecting part 211, and can be sleeved on the outer periphery of the first connecting part 211. A bearing can be provided between the first rotating part 237 and the first connecting part 211, with the bearing sleeved on the outer periphery of the first connecting part 211, and the first rotating part 237 sleeved on the outer periphery of the bearing, thereby achieving a rotatable connection between the first rotating part 237 and the first connecting part 211. The bearing reduces friction during relative rotation, improves rotational flexibility, and ensures stable power transmission.

[0119] The inner and outer rings of the bearing can axially limit the first piston 231, preventing the first rotating part 237 from moving axially along the first connecting part 211.

[0120] The second rotating part 247 is the connection point between the second piston member 241 and the second connecting part 221. The second rotating part 247 can be sleeved on the outer periphery of the second connecting part 221. Similar to the first piston member 231, the second rotating part 247 and the second connecting part 221 can also be rotatably connected by a bearing.

[0121] Please see Figure 8 and Figure 11 In some embodiments, the first connecting portion 211 and the second connecting portion 221 are arranged at a 180° phase with respect to the output shaft 110. That is, the first connecting portion 211 and the second connecting portion 221 are offset from each other and arranged at a 180° angle around the central axis of the output shaft 110. In this way, the first connecting portion 211 and the second connecting portion 221 are distributed on opposite sides of the same radial direction of the output shaft 110.

[0122] For example, when the compressor is stationary, if the first connection part 211 on the right side of the motor 100 is located on the upper side of the output shaft 110, then the second connection part 221 on the right side of the motor 100 is located on the lower side of the output shaft 110.

[0123] Please see Figure 7 Since the first connecting portion 211 and the second connecting portion 221 are set at a 180° phase relative to the output shaft 110, the offset direction of the first connecting portion 211 relative to the central axis of the output shaft 110 is exactly opposite to the offset direction of the second connecting portion 221 relative to the central axis of the output shaft 110. Thus, when the compressor is stationary, the first rotating portion 237 and the second rotating portion 247 are also set at a 180° phase relative to the output shaft 110. This results in the first piston member 231 and the second piston member 241 exhibiting opposite motion states.

[0124] When the motor 100 starts, the output shaft 110 drives the first eccentric crankshaft 210 to rotate synchronously. The first eccentric crankshaft 210 drives the first rotating part 237 of the first piston 231 to move through the first connecting part 211, thereby causing the first piston head 235 to reciprocate linearly within the first cylinder 232. At the same time, the first eccentric crankshaft 210 drives the second eccentric crankshaft 220 to rotate synchronously through the first connecting part 211. The second eccentric crankshaft 220 then drives the second rotating part 247 of the second piston 241 to move through the second connecting part 221, causing the second piston head 245 to reciprocate linearly within the second cylinder 242. This reverse linkage ensures that the reciprocating motion of the first piston 231 within the first cylinder 232 is the same as the reciprocating motion of the second piston 241 within the second cylinder 242, thus enabling the first cylinder 230 and the second cylinder 240 to be simultaneously in a state of gas suction or gas compression.

[0125] During the operation of the cylinder assembly 200, both the first eccentric crankshaft 210 and the second eccentric crankshaft 220 will generate centrifugal inertial forces due to their eccentric structures. Since the second connecting part 221 is set at a 180° phase with the first connecting part 211 relative to the output shaft 110, the centrifugal inertial forces experienced by the first piston 231 and the second piston 241 are opposite to each other.

[0126] The centrifugal inertial forces acting on the first piston 231 and the second piston 241 can form opposing force couples in the direction perpendicular to the central axis of the output shaft 110, causing the forces acting on the first piston 231 and the second piston 241 to cancel each other out. This effectively cancels out most of the centrifugal inertial forces, significantly reduces the vibration amplitude during compressor operation, reduces wear on the first piston 231, the second piston 241 and the cylinder caused by vibration, and extends the service life of the piston assembly and the entire compressor.

[0127] At the same time, the reduction in vibration amplitude can effectively reduce the noise caused by vibration, avoid noise interference to the patient's rest or nursing environment, and thus adapt to scenarios with high requirements for quiet environment such as wards and home care, thereby improving the user experience.

[0128] Furthermore, the force balance between the first piston 231 and the second piston 241 can also improve the power transmission efficiency of the compressor, avoid power loss caused by vibration, and ensure that the compression action of the first piston head 235 in the first cylinder 232 and the compression action of the second piston head 245 in the second cylinder 242 are more stable and precise. This ensures the stability of high-pressure air compression and negative pressure nitrogen discharge, provides more stable pressure support for the nitrogen-oxygen separation process of the molecular sieve device, and ensures oxygen purity and oxygen production efficiency.

[0129] To facilitate a further explanation of the relationship between the cylinder assemblies 200 on the left and right sides of the motor 100, in this embodiment, one of the two cylinder assemblies 200 is defined as the first cylinder assembly, and the other is defined as the second cylinder assembly.

[0130] Please see Figures 2 to 3 In some embodiments, the first connecting portion 211 in the first cylinder assembly and the first connecting portion 211 in the second cylinder assembly are arranged at a 180° phase relative to the central axis of the output shaft 110, so that while the first piston member 231 in the first cylinder assembly moves outward from the first cylinder body 232, the first piston member 231 in the second cylinder assembly moves inward from the first cylinder body 232.

[0131] In other words, with the common central axis of the output shafts 110 on both sides of the motor 100 as the center of rotation, in the circumferential direction of the output shaft 110, the first connecting portion 211 of the first cylinder assembly and the first connecting portion 211 of the second cylinder assembly are offset from each other, and the angle formed by the lines connecting the two first connecting portions 211 and the central axis of the output shaft 110 is 180°. Thus, the first connecting portion 211 of the first cylinder assembly and the first connecting portion 211 of the second cylinder assembly are respectively located on both radial sides of the output shaft 110.

[0132] For example, when the compressor is stationary, if the first connection part 211 on the left side of the motor 100 is located above the left output shaft 110, then the first connection part 211 on the right side of the motor 100 is located below the right output shaft 110.

[0133] When the motor 100 starts, the output shafts 110 on both sides rotate synchronously, driving the first eccentric crankshafts 210 of the first cylinder assembly and the second cylinder assembly to rotate synchronously. Since the first connecting parts 211 of the two cylinder assemblies 200 are set at a 180° phase relative to the axis of the output shaft 110, the rotational motion of the two first connecting parts 211 always remains in opposite directions and synchronous.

[0134] Specifically, when the first connecting part 211 of the first cylinder assembly rotates under the drive of the output shaft 110, it will drive the first piston 231 in the cylinder assembly 200 to move through the first rotating part 237, so that the first piston head 235 moves from inside the first cylinder body 232 toward the outside of the first cylinder body 232, that is, the first piston head 235 moves closer to the output shaft 110. At this time, the left first cylinder 230 is in the intake state, and the gas is drawn into the first cylinder body 232.

[0135] Meanwhile, please continue to refer to Figure 3 The first connecting part 211 of the second cylinder assembly rotates 180° in opposite phase to the first connecting part 211 of the first cylinder assembly. It drives the first piston 231 in the cylinder assembly 200 to move through its corresponding first rotating part 237. This causes the first piston head 235 in the second cylinder assembly to move towards the inside of the first cylinder body 232. That is, the first piston head 235 moves away from the output shaft 110. At this time, the first cylinder 230 on the right side is in a compression state, compressing or venting the gas in the cylinder body.

[0136] Thus, when the first cylinder 230 and the second cylinder 240 in the cylinder assembly 200 on one side of the motor 100 operate synchronously, the operating process of the first cylinder assembly is opposite to that of the second cylinder assembly for the cylinder assemblies 200 on both sides of the motor 100.

[0137] For example, if the first cylinder 230 and the second cylinder 240 on the left side of the motor 100 are in a gas-suction state, then the first cylinder 230 and the second cylinder 240 on the right side of the motor 100 are in a gas-compression state; or, if the first cylinder 230 and the second cylinder 240 on the left side of the motor 100 are in a gas-compression state, then the first cylinder 230 and the second cylinder 240 on the right side of the motor 100 are in a gas-suction state.

[0138] In this way, when the first cylinders 230 on both sides of the motor 100 are used for air compression, the intake and compression actions of the two first cylinders 230 can be performed alternately to ensure the continuous output of high-pressure air, avoid the interruption of gas delivery, provide continuous and stable high-pressure air support for the adsorption and desorption process of the molecular sieve device, and effectively improve oxygen production efficiency.

[0139] Meanwhile, since the first connecting parts 211 of the two cylinder assemblies 200 are set at 180° phase, the centrifugal inertial forces generated by them will also form opposite directions and cancel each other out, further optimizing the overall force balance of the compressor, reducing the vibration superposition caused by the asynchronous movement of the cylinder assemblies 200 on both sides, reducing the vibration and noise during the operation of the compressor, and further improving the operating stability of the compressor.

[0140] Furthermore, in this embodiment, by setting the first connecting portions 211 on both sides of the motor 100 at a 180° phase, the coordinated linkage of the two cylinder assemblies 200 can be achieved without the need for additional transmission adjustment components. Without increasing the size, weight, and manufacturing cost of the compressor, the continuous output of high-pressure air and the stability of compressor operation are both optimized.

[0141] Meanwhile, the alternating movement of the first piston 231 in the two cylinder assemblies 200 can effectively balance the workload of the two cylinder assemblies 200, reduce the wear of a single cylinder assembly 200, extend the service life of the piston and cylinder, and further reduce the maintenance cost of the equipment.

[0142] It should be noted that the 180-degree phase difference in this embodiment is not an absolute geometric phase difference. It can be finely adjusted within a reasonable error range according to the actual gas supply requirements and vibration control requirements. As long as the core effects of load balancing, inertial force cancellation and airflow smoothing can be achieved, it falls within the protection scope of this application.

[0143] In some embodiments, the distance between the center of the first mounting hole 213 and the central axis of the first connecting portion 211 is the first eccentric distance, and the distance between the center of the second mounting hole 223 and the central axis of the second connecting portion 221 is the second eccentric distance.

[0144] Please continue reading. Figure 7 and Figure 8 , Figure 7and Figure 8 The dotted lines in the diagram represent the central axis of the first connecting part 211, the central axis of the second connecting part 221, and the central axis of the output shaft 110.

[0145] The eccentricity determines the piston's swing and rotation stroke, thus directly affecting the compression displacement. A larger eccentricity results in a longer piston swing stroke and a larger displacement, but also increases the crankshaft radial envelope. A smaller eccentricity results in a shorter piston swing stroke and a smaller displacement.

[0146] In this embodiment, the first eccentricity distance and the second eccentricity distance are limited to 2.9~3.6mm. For small-displacement compressors, if the eccentricity distance is less than 2.9mm, the piston swing stroke is insufficient, resulting in a low compressor discharge volume, which is difficult to meet the airflow requirements of oxygen generators. If the eccentricity distance is greater than 3.6mm, although the discharge volume can be increased, it will significantly increase the radial envelope space of the crankshaft, resulting in an increase in the overall size of the compressor, which is difficult to adapt to the size requirements of oxygen generators.

[0147] In this embodiment, limiting the first eccentric distance and the second eccentric distance to 2.9~3.6mm helps ensure that the piston stroke and exhaust volume meet the airflow requirements of the portable oxygen generator, and ensures that the oxygen generation efficiency of the oxygen generator is stable at 40%-50%. At the same time, by setting the above-mentioned eccentric distance, it helps to reduce the radial space occupied by the first connecting part 211 and the second connecting part 221, and reduce the overall size of the compressor.

[0148] For example, in this embodiment, the first eccentricity distance and the second eccentricity distance can be 2.9mm, 3.1mm, 3.3mm, 3.5mm, 3.6mm, or any value between the two mentioned above, and are not specifically limited thereto. The compressor in this embodiment can be a compressor with a displacement of 1.3L, 1.4L, 1.5L, 1.6L, etc. It should be noted that this is only a partial list of embodiments, and different eccentricities do not correspond to different displacement compressors.

[0149] Please see Figure 9 and Figure 10 In some embodiments, the first eccentric crankshaft 210 includes a first counterweight 212 located on the side of the first mounting hole 213 away from the first connecting portion 211. The second eccentric crankshaft 220 includes a second counterweight 222 located on the side of the second mounting hole 223 away from the second connecting portion 221.

[0150] Since the first connecting part 211 and the second connecting part 221 are arranged at a 180° phase with respect to the output shaft 110, the first counterweight part 212 and the second counterweight part 222 are also arranged at a 180° phase with respect to the output shaft 110.

[0151] The first counterweight 212 and the first eccentric crankshaft 210, and the second counterweight 222 and the second eccentric crankshaft 220 can all adopt an integral molding structure, which helps to avoid structural loosening caused by additional assembly, ensures that the first counterweight 212 and the first eccentric crankshaft 210 and the second counterweight 222 and the second eccentric crankshaft 220 rotate synchronously, while reducing the number of parts, simplifying the assembly process, and taking into account both structural compactness and connection reliability.

[0152] Since the first counterweight 212 and the second counterweight 222 are arranged at a 180° phase with respect to the output shaft 110, when the first eccentric crankshaft 210 rotates, the centrifugal inertial force it generates is directed toward the first connecting part 211, while the first counterweight 212 is located on the other side of the output shaft 110, and the centrifugal inertial force it generates is in the opposite direction to the centrifugal inertial force mentioned above, which can initially counteract the centrifugal inertial force on the side of the first eccentric crankshaft 210.

[0153] Meanwhile, the centrifugal inertial force generated by the rotation of the second eccentric crankshaft 220 is directed toward the side of the second connecting part 221, while the second counterweight part 222 and the first counterweight part 212 are distributed on opposite sides of the output shaft 110. That is, the second counterweight part 222 and the second connecting part 221 are located on both sides of the output shaft 110, and the direction of the centrifugal inertial force generated by their rotation is opposite to the direction of the centrifugal inertial force on the side of the second eccentric crankshaft 220, thereby canceling out the centrifugal inertial force on the side of the second eccentric crankshaft 220.

[0154] Therefore, by adding the first counterweight 212 and the second counterweight 222 in this embodiment, the vibration amplitude of the compressor during high-speed operation can be effectively suppressed, the energy transmitted from vibration to the whole machine can be reduced, and the structural noise and aerodynamic noise caused by vibration can be reduced, making the compressor run more smoothly and quietly, which helps to meet the low noise requirements of oxygen production equipment.

[0155] It should be noted that the mass and center of gravity of the first counterweight 212 and the second counterweight 222 can be flexibly adjusted according to the actual eccentric mass to adapt to the design requirements of compressors with different power and size.

[0156] In some embodiments, the outer contours of the first counterweight 212 and the second counterweight 222 are arc-shaped, and the radius of the outer contour of the first counterweight 212 is less than or equal to the radius of the outer contour of the first rotating part 237, and the radius of the outer contour of the second counterweight 222 is equal to the radius of the outer contour of the second rotating part 247.

[0157] Please continue reading. Figures 9 to 11 , Figure 11 The circular dashed line in the figure shows the outer contour of the second rotating part 247.

[0158] It should be noted that when the first rotating part 237 rotates with the corresponding first eccentric crankshaft 210, the radius of the outer contour of the first rotating part 237 can be the radius of the largest circular trajectory swept by the outer contour of the first rotating part 237. When the second rotating part 247 rotates with the corresponding second eccentric crankshaft 220, the radius of the outer contour of the second rotating part 247 can be the radius of the largest circular trajectory swept by the outer contour of the second rotating part 247.

[0159] When the first counterweight 212 rotates with the first eccentric crankshaft 210, the radius of its outer contour can be the radius of the largest circular path swept by its outer contour. When the second counterweight 222 rotates with the second eccentric crankshaft 220, the radius of its outer contour can be the radius of the largest circular path swept by its outer contour.

[0160] Since the radius of the outer contour of the first counterweight 212 is less than or equal to the radius of the outer contour of the first rotating part 237, and the radius of the outer contour of the second counterweight 222 is equal to the radius of the outer contour of the second rotating part 247, the first counterweight 212 and the second counterweight 222 can avoid interference with surrounding components during the operation of the cylinder assembly 200, ensuring smooth movement of each component.

[0161] Furthermore, for small-displacement compressors, the internal space is relatively compact, making it impossible to install excessively large counterweight components. By limiting the radius of the rotating outer contour of the first counterweight 212 and the rotating outer contour of the second counterweight 222, the arc-shaped contours of the first counterweight 212 and the second counterweight 222 can obtain a larger mass moment while ensuring a small total counterweight mass, thereby achieving better balance. This effectively counteracts the centrifugal inertial force generated when the first eccentric crankshaft 210 and the second eccentric crankshaft 220 rotate, further reducing the vibration during compressor operation and preventing the vibration from being transmitted to the entire machine structure, which could lead to increased noise or component wear.

[0162] In summary, this embodiment sets the outer contours of the first counterweight 212 and the second counterweight 222 to be arc-shaped, and limits the radii of the outer contours of the first counterweight 212 and the second counterweight 222 to the radii of the outer contours of the corresponding rotating parts, which helps to achieve efficient use of space and adaptation of motion trajectory between moving parts, avoids spatial interference, and further enhances the compactness and lightweighting of the compressor.

[0163] It should be noted that the first counterweight 212 and the second counterweight 222 can have the same shape, and their specific weight and thickness can be determined according to actual design requirements. The radius of the second counterweight 222 can be the same as the radius of the outer contour of the second rotating part 247.

[0164] In some embodiments, please refer to Figure 7 The first eccentric crankshaft 210 and the first piston 231 form a first eccentric structure, and the second eccentric crankshaft 220 and the second piston 241 form a second eccentric structure. The first eccentric structure and the second eccentric structure together form a piston structure, and the center of mass of the piston structure is located on the central axis of the output shaft 110.

[0165] It should be noted that the first eccentric structure is an integral force-bearing unit composed of the first eccentric crankshaft 210, the first piston 231, and its matching connecting structures (including the first connecting part 211 and the second counterweight part 222). Similarly, the second eccentric structure is an integral force-bearing unit composed of the second eccentric crankshaft 220, the second piston 241, and its matching connecting structures (including the second connecting part 221 and the second counterweight part 222). The piston structure is a structure formed by the first eccentric crankshaft 210, the first piston 231, the second eccentric crankshaft 220, and the second piston 241. The center of mass of the piston structure is the resultant center of mass of all components in this unit, which may also include connecting parts such as bearings and set screws.

[0166] For the piston structure, its center of mass positioning needs to be calculated and optimized in conjunction with the mass distribution of the first eccentric crankshaft 210, the first piston component 231, the first connecting part 211 and the first counterweight part 212, as well as the second eccentric crankshaft 220, the second piston component 241, the second connecting part 221 and the second counterweight part 222. Among these, the center of mass calculation can be achieved through simulation software.

[0167] The piston structure formed by the first and second eccentric structures, after center of mass calculation, can have its combined center of mass fall on the central axis of the output shaft 110 by adjusting the mass ratio and center of gravity position of the first counterweight 212 and the second counterweight 222. For example, by optimizing the fan-shaped arc and mass distribution of the first counterweight 212, the eccentric mass formed by the first eccentric crankshaft 210 and the first rotating part 237 is compensated, ensuring that their mass moments cancel each other out; or, by optimizing the fan-shaped arc and mass distribution of the second counterweight 222, the eccentric mass formed by the second eccentric crankshaft 220 and the second rotating part 247 is compensated, ensuring that their mass moments cancel each other out, ultimately making the combined center of mass of the first eccentric structure coincide with the output shaft 110.

[0168] In this embodiment, when the combined centroid of the first eccentric structure and the second eccentric structure is located on the central axis of the output shaft 110, the mass moment of the first eccentric structure and the second eccentric structure is zero during high-speed rotation because their centroids coincide with the rotation center. The centrifugal inertial force is reduced to the minimum, which helps to prevent the generation of centrifugal inertial torque and thus helps the compressor to operate in a state of near vibration-free and low noise.

[0169] Meanwhile, the centrifugal inertial force of the piston structure formed by the first and second eccentric structures is reduced, which makes it easier to eliminate the additional radial load on the bearing, avoid the bearing from being worn more quickly due to long-term unbalanced load, help extend the service life of the bearing, eccentric crankshaft and compressor as a whole, and reduce equipment maintenance costs.

[0170] For example, in this embodiment, the radius of the outer contour of the second rotating part 247 of the second piston 241 is set to 13.7 mm. The second counterweight 222 can be obtained based on the radius of the outer contour of the second rotating part 247. When the outer contour radius of the second counterweight 222 is the same as the radius of the second counterweight 222, the radius of the second counterweight 222 is 27.4 / 2=13.7 mm. This size can balance the rotational inertia force of the second eccentric crankshaft 220 to the greatest extent and ensure the motion stability of the second eccentric structure.

[0171] The shape, weight, and size of the first counterweight 212 need to be considered in conjunction with the center of mass of the piston structure. By calculating and designing the shape, weight, and size of the first counterweight 212, it is helpful to make the center of mass of the piston structure located on the central axis of the output shaft 110.

[0172] Since the rotation radius of the first rotating part 237 in this embodiment is 13.7 mm, the rotation outer contour radius of the first counterweight part 212 is calculated using professional simulation software, and the radius of the first counterweight part 212 can be 11.6 mm. It should be noted that the radius of the first counterweight part 212 of 11.6 mm is not a fixed value. Its specific size will be affected by various factors such as the thickness of the first counterweight part 212, the material used, and the arc-shaped outer contour of the counterweight part. However, the maximum value of the rotation outer contour radius of the first counterweight part 212 does not exceed the rotation outer contour radius of the first rotating part 237 of 13.7 mm, so as to avoid collision and interference between the first counterweight part 212 and the first rotating part 237 when rotating, and at the same time ensure that the first counterweight part 212 can provide sufficient counterweight torque to help balance the centrifugal inertial force generated by the first eccentric structure.

[0173] Please see Figures 17 to 23 In some embodiments, the first cylinder 230 includes a first valve plate 233 located on the side of the first piston 231 away from the first eccentric crankshaft 210; the second cylinder 240 includes a second valve plate 243 located on the side of the second piston 241 away from the second eccentric crankshaft 220.

[0174] When the first piston 231 and the second piston 241 move to their extreme positions, that is, when the first piston 231 and the second piston 241 are at their maximum swing angle, interference will occur between the first piston head 235 and the first valve plate 233, and between the second piston head 245 and the second valve plate 243. This can easily cause wear on the components and affect the normal operation of the cylinder assembly 200. For example, the end of the first piston head 235 near the first valve plate 233 will move closer to the first valve plate 233. If the first valve plate 233 has a planar structure, it is easy for it to come into contact with and interfere with the end of the first piston head 235.

[0175] Based on this, at least one of the first valve plate 233 and the first piston head 235 is provided with a first clearance portion on the opposite side; at least one of the second valve plate 243 and the second piston head 245 is provided with a second clearance portion on the opposite side.

[0176] In some embodiments, please refer to Figures 17 to 20 The first valve plate 233 has a first clearance groove 234 on the side near the first piston head 235. Along the extension direction of the output shaft 110, the depth of the first clearance groove 234 gradually increases from the middle of the first valve plate 233 to the edges on both sides of the first valve plate 233. The second valve plate 243 has a second clearance groove 244 on the side near the second piston head 245. Along the extension direction of the output shaft 110, the depth of the second clearance groove 244 gradually increases from the middle of the second valve plate 243 to the edges on both sides of the second valve plate 243.

[0177] The first clearance groove 234 is formed on the end face opposite to the first valve plate 233 and the first piston head 235. Its extension direction is consistent with the extension direction of the output shaft 110, and it covers the range of motion of the piston near the valve plate when the first piston head 235 swings, ensuring that the first piston member 231 will not interfere with the first valve plate 233 during the entire swing process. The structure of the second clearance groove 244 can be the same as that of the first clearance groove 234, with only the groove size being slightly adjusted according to the size of the second piston head 245 and the swing trajectory.

[0178] When the first piston 231 and the second piston 241 swing, the swing amplitude of the two sides of the first piston head 235 is greater than that of the middle, and the swing amplitude of the two sides of the second piston head 245 is greater than that of the middle. When the two piston heads swing to the maximum angle (limit position), the two sides of the end faces of the two piston heads approach the valve plate by a greater distance. Therefore, the depth of the clearance groove increases with the direction of approaching the valve plate edge, so as to match the movement trajectory of the piston head end face, provide more clearance space for the two sides of the piston head, and at the same time ensure the structural strength and sealing performance of the middle of the valve plate.

[0179] It should be noted that the specific recess depth, increment, and extension length of the first and second clearance grooves 234 and 244 can be flexibly adjusted according to the size of the piston component, the swing angle, and the valve plate size. This effectively prevents interference between the piston and the valve plate when the piston reaches its limit position, and all of these fall within the protection scope of this application. It is understood that the installation position of the valve plate can be finely adjusted according to the overall layout of the cylinder assembly 200 to ensure no interference with components such as the piston component and the eccentric crankshaft, thus ensuring smooth operation.

[0180] like Figure 17 and Figure 19 As shown, the inclination angle of the first clearance groove 234 relative to the plate surface direction of the first valve plate 233, and the inclination angle of the second clearance groove 244 relative to the plate surface direction of the second valve plate 243 are β, and the value of β can be in the range of 1.7° to 2.0°. For example, β is 1.9°.

[0181] The first clearance groove 234 and the second clearance groove 244 in this embodiment can adapt to the swing trajectory of the first piston 231 and the second piston 241, providing clearance space for the end of the first piston head 235 near the first valve plate 233 and for the end of the second piston head 245 near the second valve plate 243, thereby ensuring smooth swing of the piston components, avoiding jamming or component wear, and extending the service life of the first piston 231, the second piston 241, the first valve plate 233 and the first valve plate 233.

[0182] Please see Figures 21 to 24 In other embodiments, the first piston head 235 of the first piston member 231 and the second piston head 245 of the second piston member 241 are both provided with a clearance structure. Specifically, the first piston head 235 is provided with a first clearance ramp 236, and the second piston head 245 is provided with a second clearance ramp 246.

[0183] In the extension direction of the output shaft 110, from the middle of the first piston head 235 to the edges on both sides of the first piston head 235, the distance between the first clearance slope 236 and the first valve plate 233 gradually increases, that is, the working surface of the first piston head 235 has an inclined structure with the middle close to the first valve plate 233 and the sides far away from the first valve plate 233, forming a slope transition.

[0184] Please see Figures 21 to 22 When the first piston 231 swings to its maximum angle, the offset of the two sides of the first piston head 235 towards the first valve plate 233 is the largest. Meanwhile, the spacing of the first clearance slope 236 increases, which ensures that there is still a sufficient gap between the two sides of the first piston head 235 and the first valve plate 233 at this time, avoiding contact interference. At the same time, it ensures that the spacing between the middle of the piston head and the first valve plate 233 is reasonable and does not affect the sealing performance of the cylinder.

[0185] The extension length of the first avoidance ramp 236 can cover the entire width of the end face of the first piston head 235 near the first valve plate 233, thereby ensuring that when the first piston head 235 swings, the end face near the first valve plate 233 can avoid interference by the ramp, without any dead angle.

[0186] like Figure 21 and Figure 25 As shown, the inclination angle of the first clearance slope 236 relative to the reference plane on which the first valve plate 233 is located can be α, where α is 1.7°~2.0°.

[0187] For example, the inclination angle of the first avoidance slope 236 can be 1.7°, 1.9°, 2.0°, etc.

[0188] Please see Figures 23 to 24 Similar to the first piston head 235, in the extending direction of the output shaft 110, from the middle of the second piston head 245 towards the edges on both sides of the second piston head 245, the distance between the second clearance slope 246 and the second valve plate 243 gradually increases. Figure 23 and Figure 26 As shown, the inclination angle of the second avoidance slope 246 relative to the horizontal plane can be α, where α is 1.7°~2.0°. The inclination angle of the second avoidance slope 246 can also be 1.7°, 1.9°, 2.0°, etc.

[0189] When the second piston 241 swings to its limit position, the offset of the two sides of the second piston head 245 towards the second valve plate 243 is at its maximum. The increasing spacing of the second clearance ramps 246 provides sufficient clearance space for the two sides, avoiding interference with the second valve plate 243. At the same time, the tilt angle and spacing parameters of the second clearance ramps 246 on both sides of the second piston head 245 can be matched with the first clearance ramp 236 to ensure the consistency of operation of the cylinder assemblies 200 on both sides and avoid operational imbalance caused by parameter deviations.

[0190] It should be noted that in this embodiment, the avoidance slope of the piston head and the avoidance groove of the valve plate can be used simultaneously in the cylinder assembly 200. The tilt direction and spacing change trend of the avoidance slope and the avoidance groove are consistent, thereby maximizing the anti-interference effect and ensuring that the sealing gap between the piston head and the valve plate is uniform, avoiding airflow leakage, and ensuring the stability of the cylinder's compression efficiency and exhaust volume.

[0191] In some embodiments, the compressor further includes an intake pipe 300 and an exhaust pipe 400.

[0192] Please see Figure 12 , Figure 12 The dashed line in the image indicates the direction of airflow.

[0193] The intake pipe 300 is used to receive airflow. The intake pipe 300 includes a first intake pipe 310 and a second intake pipe 320. The air inlets of the first cylinders 230 on both sides of the motor 100 are connected through the first intake pipe 310, and the air inlets of the second cylinders 240 on both sides of the motor 100 are connected through the second intake pipe 320.

[0194] The intake pipe 300 serves as a channel for receiving and transporting airflow. It is divided into a first intake pipe 310 and a second intake pipe 320. The two are independent of each other and do not interfere with each other. They correspond to the air intake requirements of the first cylinder 230 and the second cylinder 240, respectively, ensuring that the airflow of different functions does not interfere with each other and improving the stability of the air circuit operation.

[0195] The two ends of the first air intake pipe 310 can be sealed and connected to the air intake ports of the first cylinder 230 in the cylinder assembly 200 on both sides of the motor 100, so as to realize the connection between the air intake ports of the two first cylinders 230. This allows outside air to enter the first cylinders 230 on both sides synchronously or alternately through the first air intake pipe 310, eliminating the need to set up a separate air intake pipe 300 for each first cylinder 230, simplifying the air circuit structure and reducing the space occupied by the pipeline.

[0196] Similarly, the two ends of the second air inlet pipe 320 can be sealed and connected to the air inlet of the second cylinder 240 in the cylinder assembly 200 on both sides of the motor 100, so as to realize the connection between the air inlets of the two second cylinders 240. Its core function is to receive nitrogen from the molecular sieve device of the oxygen generation system and provide a stable airflow input channel for the second cylinder 240 to achieve negative pressure nitrogen discharge.

[0197] To ensure the air circuit sealing performance, the connection points between the first air intake pipe 310, the second air intake pipe 320 and the cylinder air intake port can all be sealed with sealing joints and sealing gaskets to avoid pressure loss or functional failure caused by airflow leakage.

[0198] The exhaust pipe 400 is used to discharge airflow. The intake pipe 300 includes a first exhaust pipe 410 and a second exhaust pipe 420. The air outlets of the first cylinders 230 on both sides of the motor 100 are connected through the first exhaust pipe 410, and the exhaust ports of the second cylinders 240 on both sides of the motor 100 are connected through the second exhaust pipe 420.

[0199] The first exhaust pipe 410 and the second exhaust pipe 420 are independent of each other, respectively corresponding to the exhaust needs of the first cylinder 230 and the second cylinder 240, so as to achieve the separation and discharge of different pressures and different types of airflow.

[0200] The first exhaust pipe 410 can be sealed and connected at both ends to the exhaust ports of the first cylinder 230 in the cylinder assemblies 200 on both sides of the motor 100, so that the high-pressure gas compressed by the first cylinders 230 on both sides can be collected and output uniformly, eliminating the need for a separate exhaust branch, simplifying the gas path layout, and ensuring that the high-pressure gas can be stably and centrally delivered to the molecular sieve device. The second exhaust pipe 420 can be sealed and connected at both ends to the exhaust ports of the second cylinder 240 in the cylinder assemblies 200 on both sides of the motor 100, so that the nitrogen gas treated by the negative pressure of the second cylinders 240 on both sides can be collected and discharged uniformly into the atmosphere, achieving efficient nitrogen discharge.

[0201] In this embodiment, outside air is received and transported to the first cylinders 230 on both sides through the first intake pipe 310. Under the oscillating compression action of the first piston head 235, the air is pressurized to form high-pressure air. Subsequently, the high-pressure air is uniformly injected into the molecular sieve device of the oxygen generation system through the first exhaust pipe 410. The molecular sieve device uses adsorption characteristics to adsorb nitrogen in the high-pressure air to achieve nitrogen-oxygen separation. The separated oxygen is collected through a special oxygen collection pipeline for subsequent oxygen demand.

[0202] The nitrogen adsorbed in the molecular sieve device needs to be desorbed. At this time, the second cylinder 240 draws out the nitrogen adsorbed in the molecular sieve device through the second air inlet pipe 320. Under the swinging action of the piston head of the second piston 241, the nitrogen is depressurized so that the pressure of the nitrogen is lower than the atmospheric pressure. The nitrogen after negative pressure treatment is then released into the atmosphere through the second exhaust pipe 420, completing the desorption and regeneration of the molecular sieve. This ensures that the molecular sieve device can continuously and stably achieve nitrogen-oxygen separation and ensure the continuity of the oxygen production process.

[0203] Regarding the operation of the first cylinder 230 and the second cylinder 240, when the first cylinder 230 and the second cylinder 240 on the left side of the motor 100 are in the compression stroke, injecting high-pressure air into the molecular sieve device for nitrogen-oxygen separation, the first cylinder 230 and the second cylinder 240 on the right side of the motor 100 can simultaneously be in the intake stroke, drawing out saturated nitrogen from the molecular sieve device through the second intake pipe 320. For the cylinder assembly on the same side of the motor 100, if the first cylinder 230 is in the intake stroke, drawing in outside air through the first intake pipe 310, the second cylinder 240 is also in the intake stroke, releasing the desorbed nitrogen into the atmosphere.

[0204] It should be noted that the specific direction and length of the intake pipe 300 and the exhaust pipe 400 can be flexibly adjusted according to the overall layout of the compressor and the installation space of the oxygen generator. This embodiment does not specifically limit this.

[0205] Please continue reading. Figure 12In some embodiments, the first intake pipe 310 and the second intake pipe 320 both include a first main pipe section 330 and two first branch pipe sections 340. The two first branch pipe sections 340 are connected to the first main pipe section 330. One of the two first branch pipe sections 340 is used to connect to the cylinder assembly 200 on one side of the motor 100, and the other is used to connect to the cylinder assembly 200 on the other side of the motor 100.

[0206] One end of the first main pipe section 330 of the intake pipe 300 is used to connect to the airflow source, and the other end is sealed to two first branch pipe sections 340 through a branch structure. Among them, the first main pipe section 330 of the first intake pipe 310 can be connected to the outside air, and the first main pipe section 330 of the second intake pipe 320 can be used to connect to the molecular sieve device of the VPSA oxygen generation system.

[0207] For the first intake pipe 310, the two first branch pipe sections 340 are respectively connected to the air inlets of the first cylinders 230 on both sides of the motor 100; for the second intake pipe 320, the two first branch pipe sections 340 are respectively connected to the air inlets of the second cylinders 240 on both sides of the motor 100.

[0208] To ensure air circuit sealing and uniform airflow distribution, the connection between the first main pipe section 330 and the two first branch pipe sections 340 adopts an integral molding or sealing welding process to avoid airflow leakage caused by segmented connection.

[0209] Meanwhile, the inner diameter of the first main pipe section 330 can be larger than the inner diameter of the two first branch pipe sections 340, ensuring that the airflow can be evenly distributed to the two branch pipe sections after entering the main pipe section, and then synchronously delivered to the corresponding cylinders on both sides, avoiding the unbalanced operation caused by uneven air intake on both sides of the cylinders.

[0210] Please continue reading. Figure 12 In some embodiments, both the first exhaust pipe 410 and the second exhaust pipe 420 include a second main pipe section 430 and two second branch pipe sections 440. Both second branch pipe sections 440 are connected to the second main pipe section 430. One of the two second branch pipe sections 440 is used to connect to the cylinder assembly 200 on one side of the motor 100, and the other is used to connect to the cylinder assembly 200 on the other side of the motor 100.

[0211] One end of the second main pipe section 430 of the exhaust pipe 400 is used to connect to the airflow output end, and the other end is sealed and connected to two second branch pipe sections 440 through a branch structure. The second main pipe section 430 of the first exhaust pipe 410 can be connected to the molecular sieve device of the VPSA oxygen generation system, and the second main pipe section 430 of the second exhaust pipe 420 can be connected to the atmospheric environment.

[0212] For the first exhaust pipe 410, the two second branch pipe sections 440 are respectively connected to the air outlets of the first cylinders 230 on both sides of the motor 100, collecting the high-pressure air compressed by the first cylinders 230 on both sides into the second main pipe section 430, and then uniformly transporting it to the molecular sieve device. For the second exhaust pipe 420, the two second branch pipe sections 440 are respectively connected to the exhaust ports of the second cylinders 240 on both sides of the motor 100, collecting the nitrogen desorbed by the second cylinders 240 on both sides into the second main pipe section 430, and then uniformly discharging it into the atmospheric environment.

[0213] The inner diameter of the second main pipe section 430 can also be larger than the inner diameters of the two second branch pipe sections 440, ensuring that the airflow discharged from the cylinders on both sides can smoothly flow into the main pipe section, avoiding airflow congestion or pressure fluctuations. The connection between the second main pipe section 430 and the second branch pipe section 440 can also adopt an integral molding or sealed welding process to ensure no airflow leakage during exhaust. Especially for the high-pressure air delivery of the first exhaust pipe 410, it can effectively reduce pressure loss and ensure the adsorption efficiency of the molecular sieve device.

[0214] Compared to the distributed interfaces and complex, circuitous layout of related technologies where each cylinder is individually connected to an air circuit, the intake pipe 300 in this embodiment, through the setting of the first main pipe section 330 and the first branch pipe section 340, as well as the setting of the second main pipe section 430 and the second branch pipe section 440, can replace multiple independent branch pipes and corresponding complex joints and sealing points, effectively reducing the number of parts and potential leakage points, thus reducing assembly difficulty and improving the sealing and reliability of the air circuit operation.

[0215] Furthermore, due to the 180-degree phase difference between the opposing connection and the opposing cylinder during operation, when the first cylinder 230 on one side of the motor 100 is in the intake stroke, the first cylinder 230 on the other side of the motor 100 may be in the end of the compression stroke or the exhaust stroke. The instantaneous flow pulses generated by the two in the common air passage can cancel each other out or smooth each other to a certain extent, thereby helping to reduce airflow pulsation and pressure fluctuation.

[0216] Please see Figures 13 to 16 In some embodiments, the compressor further includes a muffler housing 500. The muffler housing 500 has an intake passage 510 and an exhaust passage 520.

[0217] The silencing housing 500 can be a one-piece structure, and the material can be a lightweight polymer material or composite sound insulation material with excellent sound insulation and noise reduction performance. It can effectively block the transmission of internal noise to the outside, and avoid increasing its own weight and affecting the portability of the compressor.

[0218] The intake passage 510 and the exhaust passage 520 are independent of each other and not connected to each other, ensuring that the intake airflow and exhaust airflow are completely separated, and avoiding interference between the outside air and the desorbed nitrogen.

[0219] Both the intake passage 510 and the exhaust passage 520 can adopt a curved flow channel to extend the flow path of the airflow in the passage, and use airflow friction and buffering to achieve noise attenuation, while avoiding the aggravation of airflow noise caused by high-speed airflow.

[0220] The intake channel 510 is mainly used to receive outside air and deliver it to the first intake pipe 310 to suppress intake noise.

[0221] The air intake end of the air intake channel 510 is used to connect with the atmospheric environment and can be equipped with an air filter component for air purification. For example, the filter component can adopt a fine mesh structure, which can effectively filter dust, particulate matter and other impurities in the outside air.

[0222] The air outlet of the air intake passage 510 is connected to the air inlet of the first air intake pipe 310. The air outlet of the air intake passage 510 can penetrate the other side wall of the muffler housing 500 and be sealed to the air inlet of the first main section 330 of the first air intake pipe 310 through a sealing joint, so as to ensure that outside air is delivered to the first cylinders 230 on both sides through the air intake passage 510 and the first air intake pipe 310.

[0223] The exhaust channel 520 is mainly used to receive the desorbed nitrogen gas discharged from the second exhaust pipe 420, so that the nitrogen gas can be smoothly discharged into the atmosphere.

[0224] The exhaust outlet of the exhaust channel 520 can penetrate through the other side wall of the muffler housing 500 and be oriented towards the atmospheric environment. The exhaust outlet of the exhaust channel 520 can be provided with a flared structure, which helps to slow down the nitrogen emission speed, reduce the jet noise generated by high-speed exhaust, and at the same time achieve dispersed emission of nitrogen, further reducing the noise amplitude.

[0225] The intake end of the exhaust passage 520 can penetrate the side wall of the muffler housing 500 and can be sealed to the exhaust port of the second main section 430 of the second exhaust pipe 420 through a sealing joint, ensuring that all the nitrogen gas desorbed from the second cylinders 240 on both sides can flow into the exhaust passage 520.

[0226] To further improve the intake noise reduction effect, the inner wall of the muffler housing 500 can be equipped with sound insulation cotton. The sound insulation cotton can be made of porous sound-absorbing material, which can absorb the aerodynamic noise generated by the high-speed airflow.

[0227] Please see Figures 14 to 16In some embodiments, both the intake channel 510 and the exhaust channel 520 are provided with multiple partition plates 530 at intervals, which are evenly arranged along the airflow direction. The partition plates 530 can be snapped, welded, or bolted to the inner wall of the muffler housing 500. Alternatively, the partition plates 530 can also be integrally formed and connected to the inner wall of the muffler housing 500. This application does not specifically limit this aspect.

[0228] Multiple partitions 530 can divide the intake passage 510 and the exhaust passage 520 into multiple chambers, and the multiple chambers can form a multi-level noise reduction structure in the direction of airflow.

[0229] When airflow passes through the airflow channel, it sequentially passes through the noise reduction through-holes 531 on multiple partition plates 530 and enters the cavity between adjacent partition plates 530, forming multi-stage buffering and noise attenuation. When the airflow passes through the noise reduction through-hole 531 of the first partition plate 530, the airflow velocity is dispersed and slowed down, and the friction between the through-hole wall and the airflow absorbs some of the aerodynamic noise.

[0230] After the airflow enters the cavity, it forms vortices and reflections within the cavity. Noise is reflected and superimposed multiple times within the cavity, and energy is gradually consumed, achieving secondary noise attenuation. The airflow then passes through the noise reduction through-hole 531 of the next partition plate 530, repeating the above buffering and sound absorption process. After multiple stages of circulation, the noise carried by the airflow is significantly attenuated, ultimately achieving efficient suppression of intake and exhaust noise.

[0231] The adjacent partition plates 530 need to balance the noise reduction effect and the overall length of the channel. If the spacing is too large, the cavity volume will be too large, which will increase the volume of the sound-absorbing shell 500. If the spacing is too small, the cavity volume will be too small, and the noise attenuation effect will be limited.

[0232] The partition plate 530 is provided with noise reduction through holes 531. Multiple noise reduction through holes 531 can be provided, and multiple noise reduction through holes 531 with different diameters can be evenly distributed on the partition plate 530. The noise reduction through holes 531 can be circular, rhomboid, rectangular, trapezoidal, or other shapes.

[0233] To suppress noise at different frequencies, the noise-reducing through-holes 531 on different partition plates 530 can be used in combination with different aperture sizes. Small apertures generate viscous resistance (i.e., acoustic resistance) to sound waves, and the magnitude of the acoustic resistance is inversely proportional to the square of the aperture size. Based on this principle, this embodiment can employ a mixed aperture design, combined with a corresponding cavity structure, to achieve precise attenuation of noise in different frequency bands. For example, the aperture of the noise-reducing through-hole 531 can be 0.3mm to 2mm.

[0234] For example, the noise reduction through-hole 531 on the partition can be a hole with a diameter of 0.6 mm or 2 mm.

[0235] Among them, the 0.6mm micro-pore has a larger acoustic impedance. According to the characteristic that acoustic impedance is inversely proportional to the square of the aperture, it has a significant attenuation effect on high-frequency noise (frequency > 1000 Hz). It can effectively reduce the high-frequency noise components generated during the operation of the compressor, such as the noise generated by the vibration of the compressor valve plate and the turbulent high-frequency components formed by the high-speed flow of air, thus suppressing the propagation of high-frequency noise from the source.

[0236] In this embodiment, each small cavity formed by the partition plate 530 can be designed with a volume of 9~12 cm³, and the 2mm hole together with the small cavity forms a Helmholtz resonance structure. When the sound wave propagates to the opening of the noise reduction through-hole 531, the air column formed at the neck of the noise reduction through-hole 531 will reciprocate like a piston due to the sound pressure. Near the resonance frequency, the vibration velocity of the air column is the maximum, at which time the sound energy is largely converted into heat energy and consumed through viscous friction and heat loss.

[0237] In this embodiment, noise reduction through holes 531 with different apertures can also be used in combination on different partition plates 530.

[0238] The 0.6mm aperture noise-reducing via 531 can be used to eliminate high-frequency noise in the 2–5 kHz range, while the 2mm aperture noise-reducing via 531 can be used to eliminate low-frequency noise in the 500–1500 Hz range. Using these two apertures together helps achieve efficient coverage and attenuation of airflow noise across the entire frequency range.

[0239] In summary, this embodiment constructs a multi-stage buffer cavity by setting partition plates 530 with noise-reducing through holes 531 at intervals in the intake channel 510 and exhaust channel 520, thereby achieving multi-stage attenuation of airflow noise, improving the low-noise performance of the compressor, and enhancing the structural strength of the airflow channel.

[0240] Please see Figures 14 to 16 In some embodiments, the muffler housing 500 has a mounting cavity 540, the structure of which matches the shape of the circumferential outer wall of the motor 100; the mounting cavity 540 surrounds at least a portion of the motor 100.

[0241] The mounting cavity 540 can be a recessed structure, located in the middle region of the silencing housing 500, so as to match the position of the motor 100.

[0242] The overall structure of the mounting cavity 540 can be perfectly matched with the circumferential outer wall shape of at least part of the motor 100. The circumferential outer wall of the motor 100 is usually cylindrical. Therefore, the cross-section of the mounting cavity 540 can be an arc or a circle that matches the outer diameter of the motor 100. The depth of the mounting cavity 540 is set according to the size of the motor 100 and the compactness requirements to ensure that at least part of the motor 100 can be embedded in the mounting cavity 540, so as to achieve a tight fit between the motor 100 and the noise-reducing housing 500.

[0243] The motor 100 can be fixed to the mounting cavity 540 by a detachable connection method, such as by bolt fixing or snap-fit ​​connection. This facilitates the assembly and disassembly of the motor 100 and ensures the stability of the motor 100 after installation, preventing displacement of the motor 100 during operation.

[0244] The inner wall of the mounting cavity 540 may be provided with an elastic buffer sound insulation layer. This sound insulation layer is made of flexible sound insulation material and has both buffering and sound absorption functions. On the one hand, the elastic buffer layer can absorb the vibration generated by the motor 100 during operation, preventing the vibration from being transmitted to the silencing housing 500, thereby reducing the structural noise caused by vibration. On the other hand, the flexible sound insulation material can further absorb the mechanical noise generated by the motor 100, forming a synergy with the sound insulation performance of the silencing housing 500 itself, enhancing the dual noise reduction effect, and ensuring that both the operating noise of the motor 100 and the airflow noise can be effectively suppressed.

[0245] Secondly, embodiments of this application also provide an oxygen generating device, including the portable horizontally opposed oil-free four-cylinder compressor in any of the above embodiments.

[0246] It is understood that since the oxygen generating device includes the compressor in any of the above embodiments, the oxygen generating device also includes the beneficial effects of the compressor in any of the above embodiments, and therefore will not be described in detail.

[0247] In the description of this application, it should be understood that the terms “comprising” and “having” as used herein, and any variations thereof, are intended to cover non-exclusive inclusion, such that a process, method, display structure, product, or device that includes a series of steps or units is not necessarily limited to those steps or units that are expressly listed, but may include other steps or units that are not expressly listed or that are inherent to such process, method, product, or device.

[0248] The term "and / or" used in this application is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. Additionally, the character " / " in this document generally indicates that the preceding and following related objects have an "or" relationship.

[0249] Unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated.

[0250] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application.

Claims

1. A portable horizontally opposed oil-free four-cylinder compressor, characterized in that, include: The motor (100) and two sets of cylinder assemblies (200) are provided. The motor (100) includes two output shafts (110), which are respectively disposed on both sides of the motor (100) and are coaxially arranged. A cylinder assembly (200) is mounted on each of the two output shafts (110). The cylinder assembly (200) includes: A first eccentric crankshaft (210) is connected to the output shaft (110), and a first connecting part (211) is provided on the side of the first eccentric crankshaft (210) away from the motor (100). The second eccentric crankshaft (220) is connected to the first connecting part (211), and the second eccentric crankshaft (220) has the second connecting part (221) on the side away from the first eccentric crankshaft (210). The first cylinder (230) includes a first cylinder body (232) and a first piston (231). The first piston (231) includes a first piston head (235) and a first rotating part (237). The first rotating part (237) is located between the first eccentric crankshaft (210) and the second eccentric crankshaft (220). The first rotating part (237) is rotatably connected to the first connecting part (211). The second cylinder (240) includes a second cylinder body (242) and a second piston member (241). The second piston member (241) includes a second piston head (245) and a second rotating part (247). The second rotating part (247) is rotatably connected to the second connecting part (221). The central axis of the output shaft (110), the central axis of the first connecting part (211), and the central axis of the second connecting part (221) are not collinear.

2. The portable horizontally opposed oil-free four-cylinder compressor according to claim 1, characterized in that, The first connecting part (211) and the second connecting part (221) are arranged at a 180° phase relative to the output shaft (110), and the central axis of the first connecting part (211) and the central axis of the second connecting part (221) are parallel to the central axis of the output shaft (110).

3. The portable horizontally opposed oil-free four-cylinder compressor according to claim 2, characterized in that, One of the two cylinder assemblies (200) is defined as the first cylinder assembly and the other as the second cylinder assembly; The first connecting portion (211) in the first cylinder assembly and the first connecting portion (211) in the second cylinder assembly are arranged at a 180° phase with respect to the central axis of the output shaft (110), so that the first piston (231) in the first cylinder assembly and the first piston (231) in the second cylinder assembly move in opposite directions.

4. The portable horizontally opposed oil-free four-cylinder compressor according to claim 1, characterized in that, The first eccentric crankshaft (210) includes a first mounting hole (213) which is connected to the output shaft (110); the second eccentric crankshaft (220) includes a second mounting hole (223) which is connected to the first connecting part (211); The distance between the center of the first mounting hole (213) and the central axis of the first connecting part (211) is the first eccentric distance, and the distance between the center of the second mounting hole (223) and the central axis of the second connecting part (221) is the second eccentric distance. Both the first eccentric distance and the second eccentric distance are 2.9~3.6mm.

5. The portable horizontally opposed oil-free four-cylinder compressor according to claim 4, characterized in that, The first eccentric crankshaft (210) includes a first counterweight (212), which is located on the side of the first mounting hole (213) away from the first connecting part (211); The second eccentric crankshaft (220) includes a second counterweight (222), which is located on the side of the second mounting hole (223) away from the second connecting part (221); The outer contours of the first counterweight (212) and the second counterweight (222) are arc-shaped, and the radius of the outer contour of the first counterweight (212) is less than or equal to the radius of the outer contour of the first rotating part (237), and the radius of the outer contour of the second counterweight (222) is equal to the radius of the outer contour of the second rotating part (247).

6. The portable horizontally opposed oil-free four-cylinder compressor according to any one of claims 1 to 5, characterized in that, The first cylinder (230) further includes a first valve plate (233), and the second cylinder (240) further includes a second valve plate (243). At least one of the first valve plate (233) and the first piston head (235) is provided with a first clearance portion on the opposite side; And / or, at least one of the second valve plate (243) and the second piston head (245) is provided with a second clearance portion on the opposite side.

7. The portable horizontally opposed oil-free four-cylinder compressor according to claim 6, characterized in that, The first clearance portion and / or the second clearance portion is a clearance ramp or a clearance groove.

8. The portable horizontally opposed oil-free four-cylinder compressor according to any one of claims 1 to 5, characterized in that, Also includes: The intake pipe (300) includes a first intake pipe (310) and a second intake pipe (320). Both the first intake pipe (310) and the second intake pipe (320) are used to receive airflow. The air inlets of the two first cylinders (230) are connected through the first intake pipe (310), and the air inlets of the two second cylinders (240) are connected through the second intake pipe (320). An exhaust pipe (400) is used to discharge airflow. The exhaust pipe (400) includes a first exhaust pipe (410) and a second exhaust pipe (420). Both the first exhaust pipe (410) and the second exhaust pipe (420) are used to discharge airflow. The exhaust ports of the two first cylinders (230) are connected through the first exhaust pipe (410), and the exhaust ports of the two second cylinders (240) are connected through the second exhaust pipe (420).

9. The portable horizontally opposed oil-free four-cylinder compressor according to claim 8, characterized in that, It also includes a muffler housing (500), which is mounted on the outer surface of the motor (100), and the muffler housing (500) is provided with an air intake passage (510) and an exhaust passage (520). The air intake end of the air intake channel (510) is used to communicate with the outside of the muffler housing (500), and the air outlet end of the air intake channel (510) is connected to the first air intake pipe (310). The exhaust end of the exhaust passage (520) is used to communicate with the outside of the muffler housing (500), and the intake end of the exhaust passage (520) is connected to the exhaust port of the second exhaust pipe (420).

10. The portable horizontally opposed oil-free four-cylinder compressor according to claim 9, characterized in that, Both the air intake channel (510) and the exhaust channel (520) are provided with multiple partition plates (530), which divide the air intake channel (510) and the exhaust channel (520) into multiple chambers to form multi-level noise reduction; the partition plates (530) are provided with noise reduction through holes (531).

11. The portable horizontally opposed oil-free four-cylinder compressor according to claim 9, characterized in that, The silencing housing (500) has a mounting cavity (540) whose shape matches the shape of the circumferential outer wall of the motor (100); the mounting cavity (540) surrounds at least a portion of the motor (100).

12. An oxygen generating device, characterized in that, Includes the portable horizontally opposed oil-free four-cylinder compressor as described in any one of claims 1-11.

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