Compressor buffering and damping device adopting corrugated pipe system

Abstract

The invention relates to the technical field of compressor gas buffering and vibration control, and discloses a compressor buffering and damping device adopting a corrugated pipe system, which comprises an ellipsoidal tank body, an ellipsoidal containing cavity is arranged in the ellipsoidal tank body, and a gas inlet pipe and a gas outlet pipe are respectively arranged at two focal points of the ellipsoidal containing cavity; the air inlet pipe and the air outlet pipe are coaxially symmetric and are fixedly communicated with the ellipsoidal tank body; inner inserting pipes are arranged in the air inlet pipe and the air outlet pipe, each inner inserting pipe is of a corrugated pipe sleeving structure, meanwhile, a damping partition plate is installed in each inner inserting pipe, and damping holes are formed in the damping partition plates. Flanges used for fixing the inner inserting pipe are fixedly installed at an air inlet of the air inlet pipe and an air outlet of the air outlet pipe. According to the principle of an airflow buffer shock absorber, the device installation space problem is fully considered, and the device has the advantages of being simple in structure, ingenious in design, small in pressure loss, low in cost, high in adaptability, high in manufacturing and installation operability, convenient to install and use and the like.

Description

Technical Field

[0001] The present invention relates to the technical field of compressor gas buffering and vibration control, and in particular to a compressor buffering and vibration reduction device using a bellows system. Background Art

[0002] The compressor has the characteristic of intermittent intake and exhaust, which causes the gas at the inlet and exhaust ports of the cylinder to be in a pulsating state, that is, the pressure and velocity show periodic changes. When the pulsating airflow flows through a pipe with a non-constant cross-section, an exciting force will be generated, causing the pipe to be forced to vibrate. The structural vibration and noise problems generated by the compressor system during operation seriously affect its application. The core of pipeline vibration control is to suppress the airflow pulsation in the pipeline. The conventional method to suppress airflow pulsation is to adjust the volume of the tank and add an orifice plate inside the tank; the common method of structural vibration control is to add support to the parts with larger vibrations. The above vibration control method does not fully consider the multi-cylinder and multi-stage nature of the compressor and the phase of the pulsating gas, and the effect of suppressing airflow pulsation is poor.

[0003] Publication No. CN113266553A describes a compressor tank device comprising a tank, a filter tube, and an orifice plate. An inlet pipe, a baffle, a filter tube, and an orifice plate are installed within the tank's internal chamber. This allows pulsating gas to flow through the inlet pipe into each independent air chamber for adequate buffering before entering each chamber's filter tube and converging into the independent chamber. This prevents the superposition of pulsating gases in phase. The orifice plate ultimately modifies the gas waveform, further reducing airflow pulsation. The tank vibrates during this pulsation suppression process, and this vibration is controlled by three automatically height-adjustable buttresses.

[0004] Based on the above technical features, the problem that arises is that in the existing technology, due to the installation of partitions, orifice plates and filter tubes inside the tank body, the air flow pressure drop loss increases, and the device is bulky and occupies a large area.

[0005] Therefore, it is necessary to solve the above problems by using a compressor buffer vibration reduction device adopting a bellows system. Summary of the Invention

[0006] The object of the present invention is to provide a compressor buffer vibration reduction device using a bellows system to solve the problems raised in the above background technology.

[0007] To achieve the above-mentioned purpose, the present invention provides the following technical solutions: a compressor buffer vibration reduction device adopting a bellows system, comprising an ellipsoidal tank body, an ellipsoidal cavity is arranged in the ellipsoidal tank body, an air inlet pipe and an air outlet pipe are respectively arranged at the two foci of the ellipsoidal cavity, the air inlet pipe and the air outlet pipe are coaxially symmetrical and are fixedly connected to the ellipsoidal tank body; inner tubes are arranged inside the air inlet pipe and the air outlet pipe, each inner tube adopts a bellows suit structure, and a damping baffle is installed in each inner tube, and a damping hole is opened on the damping baffle; flanges for fixing the inner tubes are fixedly installed at the air inlet of the air inlet pipe and the air outlet of the air outlet pipe.

[0008] Preferably, the inner tube includes a first bellows and a second bellows, the length of the first bellows is greater than that of the second bellows; the first bellows is sleeved on the second bellows, and an annular space curved channel is constructed between the first bellows and the second bellows.

[0009] Preferably, the first bellows and the flange are an integrally formed assembly, and the second bellows are fixedly connected to the flange.

[0010] Preferably, a damping baffle is fixedly installed at the movable pipe openings of the first bellows and the second bellows.

[0011] Preferably, the flange on the air inlet pipe is connected to a first expansion joint, and the flange on the air outlet pipe is connected to a second expansion joint.

[0012] Technical effects and advantages of the present invention: First, the present invention utilizes the principle of an airflow buffer to expand, decelerate, buffer, divert, and stabilize pulsating, impactful airflow, reducing pulsation and impact energy, and promoting smooth, stable airflow. Furthermore, it fully considers equipment installation space constraints, resulting in a simple structure, ingenious design, minimal pressure loss, low cost, strong adaptability, and easy manufacturing and installation.

[0013] Secondly, the present invention adopts a bellows suit structure as a buffer component, which has good vibration reduction and noise reduction effects, and can also be used for vibration reduction and noise reduction of gas pipelines of other equipment. BRIEF DESCRIPTION OF THE DRAWINGS

[0014] Figure 1 This is a schematic diagram of the three-dimensional disassembled structure of the present invention; Figure 2 This is a schematic diagram of a half-section structure of the present invention; Figure 3 It is a partial half-section schematic diagram of the present invention; Figure 4 It is a side perspective schematic diagram of the present invention; Figure 5It is a schematic radial side view of the damping baffle of the present invention; Figure 6 This is a schematic axial front view of the damping baffle of the present invention; Figure 7 Schematic diagram of air flow pulsation curves in each flow channel before attenuation according to the present invention; Figure 8 Schematic diagram comparing the airflow waveform d1 of the present invention and the airflow waveform d2 of the prior art.

[0015] In the figure: 1. Ellipsoidal tank body; 2. Air inlet pipe; 3. Air outlet pipe; 4. First bellows; 5. Second bellows; 6. Damping baffle; 7. Flange; 8. Cross rod; 9. First expansion joint; 10. Second expansion joint. DETAILED DESCRIPTION

[0016] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative work are within the scope of protection of the present invention.

[0017] The present invention provides Figures 1 to 8 The illustrated compressor vibration damping device employing a bellows system includes an ellipsoidal tank body 1. Within the ellipsoidal tank body 1, a matching ellipsoidal cavity is positioned to effectively cushion the airflow. The ellipsoidal cavity's structure alters the direction, path, and waveform of the gas, creating a 180° phase difference between the gas discharged from different exhaust cylinders of the compressor. This prevents the overlapping of pulsating gas peaks and modifies the waveform to suppress airflow pulsation. This reduces pipeline vibration, while gas expansion partially eliminates aerodynamic noise.

[0018] The ratio of the major axis to the minor axis of the ellipsoidal tank body 1 is between 1.5:1 and 2.5:1 to ensure better use effect. In the actual manufacturing process, the volume of the ellipsoidal tank body 1 can be set as needed to adapt to different use conditions.

[0019] An air inlet pipe 2 and an air outlet pipe 3 are located at the two focal points of the ellipsoidal cavity. Both are located along the long axis of the ellipsoidal tank body 1 and are coaxially symmetrically distributed. Both extend through the ellipsoidal tank body 1 and are fixedly connected to it, thereby forming a gas flow path.

[0020] A flange 7 is fixedly mounted at the air inlet of the air inlet pipe 2 and the air outlet of the air outlet pipe 3, and both flanges 7 are located outside the ellipsoidal tank body 1. An inner insert is fixedly mounted on each flange 7, and an inner insert is coaxially inserted into each of the air inlet pipe 2 and the air outlet pipe 3.

[0021] The flange 7 on the intake pipe 2 is connected to a first expansion joint 9 via a flange-to-flange connection. This first expansion joint 9 consists of an expansion tube with an expansion chamber within it. The gas discharged from the compressor's exhaust cylinder, which contains aerodynamic noise, flows into the expansion chamber of the first expansion joint 9 and expands in volume. This reduces the peak pulsation of the airflow, minimizing the impact of the pulsating airflow on the intake pipe 2 and damage to the internal cannula, while also reducing pipeline vibration noise. Furthermore, the gas expansion also partially eliminates aerodynamic noise.

[0022] Flange 7 on outlet pipe 3 is connected to a second expansion joint 10 via a flange-to-flange connection. Second expansion joint 10 has the same structure as first expansion joint 9. After gas discharged from outlet pipe 3 flows into the expansion chamber within second expansion joint 10, it expands and gradually reaches a stable state, thereby stabilizing the airflow and balancing the flow rate, resulting in a smooth and stable outflow.

[0023] Both inner tubes adopt a bellows set structure, relying on the bellows' own elasticity to offset the low-frequency air pressure pulsation force in the air flow pulsation, thereby reducing pipeline vibration and noise.

[0024] Each inner tube includes a first bellows 4 and a second bellows 5. The first bellows 4 is thicker and longer than the second bellows 5. The first bellows 4 is sleeved over the second bellows 5. The first bellows 4 and flange 7 are integrally molded, and the second bellows 5 is fixedly connected to the flange 7 via a cross bar 8.

[0025] The expansion tube radius of the first expansion joint 9 and the second expansion joint 10 are both twice the tube opening radius of the air inlet of the second bellows 5 .

[0026] Part of the gas flowing into the inlet pipe 2 and the outlet pipe 3 flows along the second bellows 5, the internal channel of which is called the main channel. The other part flows along the curved annular channel formed between the first bellows 4 and the second bellows 5, which is called the side channel.

[0027] A damping baffle 6 is fixedly connected to the movable pipe openings of the first bellows 4 and the second bellows 5, that is, the pipe openings away from the connected flange 7. The damping baffle 6 is generally in the shape of a cone cover, and the protrusions are all facing the ellipsoidal cavity inside the ellipsoidal tank 1.

[0028] Each damping baffle 6 covers the corresponding pipe opening and is provided with multiple staggered damping holes of varying sizes. The damping holes of the same size are evenly spaced along the circumference of the damping baffle 6. These holes not only guide the flow but also act as a buffer, providing a certain degree of damping and dissipation, attenuating high-frequency airflow pulsations.

[0029] The damping baffles 6 connected to the two first bellows 4 are located at the two foci of the ellipsoidal cavity, and each damping hole on the damping baffles 6 connected to the two first bellows 4 is arranged at an angle. The damping holes on the damping baffles 6 connected to the first bellows 4 located in the inlet pipe 2 are used to radiate gas into the ellipsoidal cavity, while the damping holes on the damping baffles 6 connected to the first bellows 4 located in the outlet pipe 3 are used to disperse the converged gas into multiple parallel airflows.

[0030] The entire device adopts a compact frame structure to integrate multiple pulsation attenuation methods within a limited space.

[0031] Working principle: When in use, the gas discharged from different exhaust cylinders of the compressor flows into the first expansion joint 9 connected to the intake pipe 2. At this time, the gas containing aerodynamic noise expands, the volume increases, and the peak value of the airflow pulsation decreases.

[0032] Then, the gas with reduced pulsation peak value flows into the intake pipe 2. The gas entering the intake pipe 2 flows along the main flow channel inside the second bellows 5 and the side flow channel constructed between the first bellows 4 and the second bellows 5.

[0033] When gas flows along the main channel and the side channel, based on the basic principle of acoustic interference, the main channel and side channels of different lengths are formed because the first bellows 4 and the second bellows 5 are nested and the first bellows 4 is longer than the second bellows 5. The side channel is longer than the main channel.

[0034] The excitation forces generated by the air flow pulsations with opposite phases in the two flow channels on the tube bodies of the first bellows 4 and the second bellows 5 are superimposed and offset each other, thereby maximally attenuating the excitation forces on the first bellows 4 and the second bellows 5 and reducing vibration noise.

[0035] Specifically, because the main channel is shorter than the side channel, gas with a certain amount of airflow pulsation, i.e., pressure fluctuation, will partially reach the ellipsoidal cavity within the ellipsoidal tank body 1 through the main channel, while the remaining portion will arrive later through the side channel. When the gas in the side channel reaches the ellipsoidal cavity within the ellipsoidal tank body 1, its airflow pulsation will lag in phase with the gas arriving through the main channel.

[0036] When the airflow pulsation of the gas flowing into the ellipsoidal cavity through the side channel, i.e., the side channel airflow pulsation, lags behind the airflow pulsation of the gas reaching the ellipsoidal cavity through the main channel, i.e., the main channel airflow pulsation, by 180 degrees, the gases from the two channels in the ellipsoidal cavity cancel each other out due to the opposite phases of the airflow pulsation, thereby achieving the purpose of actively attenuating the airflow pulsation.

[0037] At this time, because the transmission of sound waves is periodic, when the phase of the airflow pulsation of the gas reaching the ellipsoidal cavity through the side channel lags behind the airflow pulsation of the gas reaching the ellipsoidal cavity through the main channel by an odd multiple of 180 degrees, the gases in the two flow channels can cancel each other out when reaching the ellipsoidal cavity due to the opposite phases of the airflow pulsation, thereby achieving the purpose of correspondingly attenuating the airflow pulsation of this device.

[0038] The length difference between the main channel and the side channel can be determined based on the airflow pulsation frequency. The compressor's fundamental frequency of airflow pulsation is specifically related to factors such as the number of teeth on the screw compressor's male rotor, the screw compressor's profile, and the speed of the screw compressor's male rotor. In summary, the side channel designed between the first bellows 4 and the second bellows 5 can effectively attenuate the fundamental frequency of airflow pulsation and its odd-numbered multiples, such as the 1st, 3rd, and 5th multiples.

[0039] Due to the distance difference between the main channel and the side channel, there is a time difference. When the distance difference between the main channel length and the side channel length is half a cycle of the airflow pulsation frequency to be attenuated, that is, the phase difference is 180 degrees, due to the opposite phases, the airflows in the two channels are superimposed on each other when they converge, and the airflow pulsation amplitude is attenuated and offset each other, thereby achieving the purpose of reducing vibration noise.

[0040] As the gas in the main channel flows through the damping baffle 6 connected to the first bellows 4, it impacts this baffle 6, dissipating the pulsation energy of the airflow to varying degrees. The gas in the main channel and the gas in the branch channel then converge between the two damping baffles 6 in the intake pipe 2. The converged gas radiates into the ellipsoidal cavity through the damping baffle 6 connected to the second bellows 5. During this process, the converged gas impacts this damping baffle 6, again dissipating the pulsation energy of the airflow to varying degrees.

[0041] At the same time, when the gas impacts the damping baffle 6, the damping baffle 6 drives the first bellows 4 and the second bellows 5 to expand and contract, and the damping baffle 6 moves forward and backward, thereby changing the volume of the ellipsoidal cavity.

[0042] The ellipsoidal cavity is used as a chamber to eliminate noise. Due to the change in the position of the damping baffle 6, the air flow pulsation flowing through the main channel and the side channel will form a phase difference, thereby adjusting the silencing frequency of the ellipsoidal cavity, increasing the frequency range of the attenuated air flow pulsation, and improving the air flow pulsation reduction rate of the device.

[0043] Next, the gas entering the ellipsoidal tank 1 is refracted and reflected by the inner wall of the tank 1, converging at the focal point of the ellipsoidal cavity where the outlet pipe 3 is located. During this process, the sound waves refracted by the inner wall of the ellipsoidal tank 1 change their waveform and phase, thereby altering their transmission characteristics. When the sound waves overlap at the focal point of the ellipsoidal cavity where the outlet pipe 3 is located, due to the wide frequency band of the radiated noise, the mutually anti-phase sound waves suppress and cancel each other, preventing the superposition of pulsating gas with the same phase, thereby effectively reducing and weakening the sound wave intensity.

[0044] The converged gas then flows into the outlet pipe 3. During this process, the gas first flows through the damping baffle 6 on the first corrugated tube 4. At this time, the damping baffle 6 is similar to a rectifying grid, and the converged gas is rectified into multiple parallel airflows, further reducing the unevenness of the airflow fluctuations.

[0045] Multiple airflows then flow along the main and branch channels, respectively, reducing airflow pulsation for a second time. After offsetting and reducing these pulsations, the airflows converge again at the outlet of outlet pipe 3 for a third reduction. This achieves the goal of improving air flow buffering and attenuating airflow pulsation by utilizing the multi-stage pressure reduction principle. This effectively addresses the vibration and noise issues caused by airflow pulsation impacting the pipeline.

[0046] Finally, the gas gathered at the outlet of the gas outlet pipe 3 flows into the second expansion joint 10, where it expands and increases in volume. This releases the energy within the gas, causing it to gradually reach a stable state, thereby stabilizing the airflow and balancing the flow rate. The air then flows out of the second expansion joint 10 smoothly and steadily.

[0047] Finally, it should be noted that the above is only a preferred embodiment of the present invention and is not intended to limit the present invention. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art can still modify the technical solutions described in the aforementioned embodiments or make equivalent substitutions for some of the technical features therein. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.

Claims

1. A compressor buffer vibration reduction device using a bellows system, comprising an ellipsoidal tank body (1), characterized in that: An ellipsoidal cavity is provided in the ellipsoidal tank body (1), and an air inlet pipe (2) and an air outlet pipe (3) are respectively provided at two foci of the ellipsoidal cavity, the air inlet pipe (2) and the air outlet pipe (3) are coaxially symmetrical and are both fixedly connected to the ellipsoidal tank body (1); an inner tube is provided inside the air inlet pipe (2) and the air outlet pipe (3), each inner tube adopts a bellows sleeve structure, and a damping baffle (6) is installed in each inner tube, and a damping hole is opened on the damping baffle (6); a flange (7) for fixing the inner tube is fixedly installed at the air inlet of the air inlet pipe (2) and the air outlet of the air outlet pipe (3).

2. The compressor buffer vibration reduction device using a bellows system according to claim 1, characterized in that: The inner tube comprises a first bellows (4) and a second bellows (5), wherein the length of the first bellows (4) is greater than the length of the second bellows (5); the first bellows (4) is sleeved on the second bellows (5), and an annular curved channel is constructed between the first bellows (4) and the second bellows (5).

3. The compressor buffer vibration reduction device using a bellows system according to claim 2, characterized in that: The first bellows (4) and the flange (7) are an integrally formed assembly, and the second bellows (5) is fixedly connected to the flange (7).

4. The compressor buffer vibration reduction device using a bellows system according to claim 3, characterized in that: A damping baffle (6) is fixedly mounted at the movable pipe openings of the first bellows (4) and the second bellows (5).

5. The compressor buffer vibration reduction device using a bellows system according to claim 1, characterized in that: The flange (7) on the air inlet pipe (2) is connected to a first expansion joint (9), and the flange (7) on the air outlet pipe (3) is connected to a second expansion joint (10).

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