Gas-driven double-blade type rotary swing motor and use method thereof

Abstract

The invention discloses a gas-driven double-blade type rotary swing motor and a using method, and relates to the technical field of pneumatic driving. The air compressor comprises a rotating shaft, an air storage cylinder body, a cylinder body front end cover and a cylinder body rear end cover, a first stator blade and a second stator blade are symmetrically arranged on the inner side of the air storage cylinder body, and a first rotor blade and a second rotor blade are symmetrically arranged on the two sides of the rotating shaft; the first air cavity channel and the second air cavity channel are formed in the two sides of the two different sections of the first rotor blade and the second rotor blade respectively, so that air cavities on the opposite sides are communicated, the structure is simple and compact, the size and weight are small, the manufacturing cost is low, high-pressure sealing between the air cavities can be ensured, and the high-torque rotating and swinging device can be used for various occasions needing high-torque rotating and swinging.

Description

Technical Field

[0001] The present invention belongs to the technical field of pneumatic drive, and particularly relates to a gas-driven double-vane rotary oscillating motor and a usage method thereof. Background Art

[0002] In the fields of industrial automation, mechanical engineering, and vehicle suspension systems, reciprocating rotary oscillating mechanisms, as a common form of motion, are widely used in scenarios that require periodic angle adjustment or dynamic balance control. Traditional reciprocating rotary oscillating mechanisms mainly rely on hydraulic drive or motor drive solutions. Although these technologies are relatively mature, there are still significant technical bottlenecks in practical applications:

[0003] Deficiencies of hydraulic drive systems: Hydraulic systems need to be equipped with high-pressure pumps, liquid storage tanks, complex pipelines, and sealing structures, resulting in a large overall volume, a relatively complex system, high installation and maintenance costs. At the same time, during long-term use, the aging of seals is likely to cause hydraulic oil leakage, which not only pollutes the environment but also reduces the drive efficiency due to pressure loss. Moreover, the compressibility of hydraulic media and the pipeline pressure transmission delay limit the dynamic response speed of the system, especially in scenarios of frequent start-stop or rapid adjustment.

[0004] Deficiencies of motor drive systems: There are volume and weight limitations. Under high torque requirements, the volume of motors and reduction mechanisms increases significantly, making it difficult to meet the requirements of lightweight design. And under high-load conditions, the energy consumption of motors increases sharply, and heat dissipation problems may cause overheat protection shutdown, affecting the reliability of the system. At the same time, the environmental adaptability is poor. In humid, dusty, or high-temperature environments, the motor windings and electronic components are easily eroded or fail, restricting their application in harsh working conditions.

[0005] In recent years, pneumatic drive technology has been widely used in the field of industrial automation due to its advantages such as clean medium, simple structure, and strong anti-pollution ability. However, existing pneumatic actuators (such as cylinders and pneumatic motors) still have the following disadvantages when directly applied to reciprocating rotary oscillating mechanisms: The control accuracy of reciprocating rotary oscillation is insufficient. Traditional pneumatic components mainly rely on the conversion of linear motion and it is difficult to achieve direct drive of high-precision angular oscillation. At the same time, the output torque is limited, the air pressure-mechanical energy conversion efficiency is low, and it is difficult to match the torque output ability of hydraulic or motors under the same volume. There is a balance problem between the rapidity of air pressure adjustment and the pressure fluctuation during load mutation, which easily leads to instability during the oscillation process and poor stability.

[0006] Therefore, in summary, hydraulic and motor drive systems have shortcomings in reliability, efficiency, and environmental adaptability under complex working conditions, while traditional pneumatic actuators cannot calculate their output torque, making it difficult to match the corresponding hydraulic pressure and unable to meet the dual requirements of high torque and precise angular oscillation.

[0007] In response to this, we design a gas-driven double-vane rotary oscillating motor and its usage method to solve the above problems. Summary of the Invention

[0008] To solve the above technical problems, the present invention is achieved through the following technical solutions:

[0009] The present invention is a gas-driven double-vane rotary oscillating motor, including a rotating shaft, a gas storage cylinder block, a front cylinder head cover, and a rear cylinder head cover. The inner wall of the gas storage cylinder block is symmetrically provided with a first stator vane and a second stator vane. The first stator vane, the second stator vane, and the gas storage cylinder block are of an integral structure. On the side of the first stator vane and the second stator vane away from the inner wall of the gas storage cylinder block, a first stator sealing groove and a second stator sealing groove are respectively opened. Between the rotating shaft and the first stator sealing groove and the second stator sealing groove, stator sealing sheets are provided.

[0010] On both sides of the rotating shaft, a first rotor vane and a second rotor vane are symmetrically provided. The first rotor vane, the second rotor vane, and the rotating shaft are of an integral structure. On the side of the first rotor vane and the second rotor vane away from the rotating shaft, a first rotor sealing groove and a second rotor sealing groove are respectively opened. Between the inner wall of the gas storage cylinder block and the first rotor sealing groove and the second rotor sealing groove, rotor sealing sheets are provided. The rotating shaft is installed inside the gas storage cylinder block, and the first stator vane, the second stator vane, the first rotor vane, and the second rotor vane are arranged in a cross pattern.

[0011] At both ends of the gas storage cylinder block, cylinder block sealing grooves are provided. On the side of the middle protrusion of the front cylinder head cover, an outer front cover sealing groove is provided. The cylinder block sealing groove close to the front cylinder head cover and the outer front cover sealing groove cooperate with each other. On the side of the middle protrusion of the rear cylinder head cover, an outer rear cover sealing groove is provided. The cylinder block sealing groove close to the rear cylinder head cover and the outer rear cover sealing groove cooperate with each other. Between the cylinder block sealing grooves on both sides and the outer front cover sealing groove and the outer rear cover sealing groove, cylinder block sealing rings are provided.

[0012] The front cylinder head cover is penetrated and provided with a first air inlet hole, a second air inlet hole, a first exhaust hole, and a second exhaust hole. Inside the gas storage cylinder block, a first air pressure chamber, a second air pressure chamber, a third air pressure chamber, and a fourth air pressure chamber are sequentially arranged. The first air pressure chamber, the second air pressure chamber, the third air pressure chamber, and the fourth air pressure chamber are separated by the first stator vane, the second stator vane, the first rotor vane, and the second rotor vane. The first air inlet hole corresponds to the first air pressure chamber, the second air inlet hole corresponds to the second air pressure chamber, the first exhaust hole corresponds to the third air pressure chamber, and the second exhaust hole corresponds to the fourth air pressure chamber. At the outer ends of the first air inlet hole, the second air inlet hole, the first exhaust hole, and the second exhaust hole, air plug interfaces are threadedly provided.

[0013] On one side of the first stator vane, a cylinder positioning hole for the positioning and assembly of the front end cover of the cylinder block and the gas storage cylinder block is provided. On the front end cover of the cylinder block, an end cover positioning hole is provided. The end cover positioning hole cooperates with the cylinder positioning hole, and a positioning pin is provided between the end cover positioning hole and the cylinder positioning hole.

[0014] On one end of the gas storage cylinder block, a plurality of threaded holes for connecting the gas storage cylinder block and the rear end cover of the cylinder block are provided. The rear end cover of the cylinder block is in interference connection with the gas storage cylinder block. A plurality of threaded through holes are provided in the protruding part of the rear end cover of the cylinder block. The threaded holes correspond to the threaded through holes one by one and cooperate with each other, and screws are threadedly arranged between the threaded holes and the corresponding threaded through holes.

[0015] On one side of the outer wall of the rotating shaft, a first rotating shaft sealing groove and a second rotating shaft sealing groove are provided. On the inner surface of the front end cover of the cylinder block, two inner sealing grooves of the front end cover are provided. A first shaft sealing ring is provided between the inner sealing groove of the front end cover and the first rotating shaft sealing groove. A second shaft sealing ring is provided between the inner sealing groove of the front end cover and the second rotating shaft sealing groove. On the other side of the outer wall of the rotating shaft, a third rotating shaft sealing groove and a fourth rotating shaft sealing groove are provided. On the inner surface of the rear end cover of the cylinder block, two inner sealing grooves of the rear end cover are provided. A third shaft sealing ring is provided between the inner sealing groove of the rear end cover and the third rotating shaft sealing groove. A fourth shaft sealing ring is provided between the inner sealing groove of the rear end cover and the fourth rotating shaft sealing groove.

[0016] On one side surface of the first rotor vane, a first air chamber channel is provided. The first air chamber channel penetrates to the other side of the second rotor vane. On the other side surface of the first rotor vane away from the first air chamber channel, a second air chamber channel is provided. The second air chamber channel penetrates to the other side of the second rotor vane. Both the first air chamber channel and the second air chamber channel are inclined structures. The first air chamber channel and the second air chamber channel are at the intersection position of two different cross-sections of the rotating shaft. Both ends of the first air chamber channel are respectively communicated with the first air pressure chamber and the fourth air pressure chamber. Both ends of the second air chamber channel are respectively communicated with the second air pressure chamber and the third air pressure chamber.

[0017] At positions near both ends of the rotating shaft, a first keyway and a second keyway are respectively provided. On both sides of the outer wall of the rotating shaft, a first ball bearing and a second ball bearing are respectively installed. The first ball bearing is arranged between the rotating shaft and the front end cover of the cylinder block. The second ball bearing is arranged between the rotating shaft and the rear end cover of the cylinder block.

[0018] On one side of the surface of the rotating shaft close to the first keyway, a first gasket groove is provided. On one side of the surface of the rotating shaft close to the second keyway, a second gasket groove is provided. Limiting gaskets are arranged in both the first gasket groove and the second gasket groove. The two limiting gaskets cooperate with the first ball bearing and the second ball bearing respectively. The first shaft seal ring, the second shaft seal ring, the third shaft seal ring, the fourth shaft seal ring, the cylinder block seal ring, the rotor sealing piece and the stator sealing piece are all made of polytetrafluoroethylene material. The rotating shaft is supported and fixed inside the storage cylinder block by the first rotor blade, the second rotor blade, the front end cover of the cylinder block and the rear end cover of the cylinder block on the shaft. The rotating shaft on one side of the front end cover of the cylinder block can be welded to the remaining external shaft through a sleeve. The rear end cover of the cylinder block can be welded to the remaining external shaft.

[0019] A method for using a gas-driven double-blade rotary swing motor includes the following steps:

[0020] Step 1: Calculate the volume change of a single chamber. First, obtain the corresponding parameters. The initial volume of a single chamber of the first pneumatic chamber, the second pneumatic chamber, the third pneumatic chamber and the fourth pneumatic chamber is:

[0021]

[0022] R: Inner radius of the cylinder block (R = D / 2, D is the inner diameter of the cylinder block);

[0023] r: Radius of the output shaft (r = d / 2, d is the diameter of the output shaft).

[0024] The volume change ΔV of a single chamber should be:

[0025] ΔV = arc length · H · L = R eff ·θ·H·L

[0026] Where:

[0027] H = R - r is the blade height;

[0028] L is the axial length of the cylinder block;

[0029] θ is the swing angle of the rotor blade;

[0030] R eff is the distance from the pressure center to the rotating shaft

[0031] Step 2: Calculate the pressure difference and torque. Based on the volume change ΔV, the pressures of the high-pressure chamber and the low-pressure chamber are respectively:

[0032]

[0033] The effective pressure difference is:

[0034]

[0035] The torque formula is as follows:

[0036] T(θ) = η·ΔP(θ)·A·R eff

[0037] Wherein, the effective acting area A of the blade = H·L;

[0038] η is the mechanical efficiency after losses caused by gas seal leakage, etc.;

[0039] V0 is the initial single - chamber volume;

[0040] P0 is the initial single - chamber pressure;

[0041] The final torque formula

[0042]

[0043] Where T friction is the frictional torque generated by the rotation of the rotor blade;

[0044] Step 3: According to the required reciprocating swing angle, combined with the calculated actual output torque, match the corresponding air pressure.

[0045] The present invention has the following beneficial effects:

[0046] The present invention fixes the rotating shaft in the air storage cylinder through the front end cover and the rear end cover of the cylinder block. At the same time, high - pressure gas is filled through the first air inlet hole, the second air inlet hole, the first exhaust hole and the second exhaust hole, so that different air pressures are filled in the first air pressure chamber, the second air pressure chamber, the third air pressure chamber and the fourth air pressure chamber in the air storage cylinder, thereby driving the first rotor blade and the second rotor blade to swing, and then driving the rotation of the rotating shaft, so as to achieve the purpose of pneumatic - driven rotation and swing;

[0047] Among them, the first shaft - used sealing ring, the second shaft - used sealing ring, the third shaft - used sealing ring, the fourth shaft - used sealing ring, the cylinder - block sealing ring, the rotor sealing piece and the stator sealing piece ensure the sealing inside the device, avoid air leakage, and can well improve the utilization efficiency of gas. The overall structure is simple and compact, easy to manufacture, small in volume and weight, low in manufacturing cost, and can provide a large torque through the utilization of air pressure, suitable for various occasions requiring large - torque rotation and swing. And the rotating shaft on one side of the front end cover of the cylinder block is welded to the other external shaft through a sleeve, and the rear end cover of the cylinder block can be welded to the other external shaft, so that the invention can have a high adaptability, can be applied in various environments, and at the same time, the utilization of gas reduces environmental pollution;

[0048] Meanwhile, the torque required for the motor output is calculated based on the angle of swing as needed, and then the corresponding air pressure is matched, which can meet different usage scenarios, achieve the purpose of high-precision reciprocating swing, and effectively improve the applicable range and usage effect of the motor.

[0049] Of course, it is not necessary for any product implementing the present invention to simultaneously achieve all the above-mentioned advantages. BRIEF DESCRIPTION OF THE DRAWINGS

[0050] In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the following will briefly introduce the drawings required for the description of the embodiments. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, other drawings can be obtained based on these drawings without creative efforts.

[0051] Figure 1 is a three-dimensional structure diagram of the present invention;

[0052] Figure 2 is a structure diagram of the front end cover of the cylinder block of the present invention;

[0053] Figure 3 is a structure diagram of the rear end cover of the cylinder block of the present invention;

[0054] Figure 4 is a structure diagram of the rotating shaft of the present invention;

[0055] Figure 5 is a structure diagram of the first ball bearing and the second ball bearing assembled on the rotating shaft of the present invention;

[0056] Figure 6 is a structure diagram of the first air chamber passage of the present invention;

[0057] Figure 7 is a structure diagram of the second air chamber passage of the present invention;

[0058] Figure 8 is a structure diagram of the air storage cylinder block of the present invention;

[0059] Figure 9 is a side structure diagram of the present invention;

[0060] Figure 10 is a cross-sectional view of the present invention with the front end cover of the cylinder block removed.

[0061] In the drawings, the list of components represented by each reference numeral is as follows:

[0062] 1. Cylinder head end cover; 2-a. First intake hole; 2-b. Second intake hole; 2-c. First exhaust hole; 2-d. Second exhaust hole; 3-a. First air pressure chamber; 3-b. Second air pressure chamber; 3-c. Third air pressure chamber; 3-d. Fourth air pressure chamber; 4. Air plug interface; 5. End cover positioning hole; 6. Positioning pin; 7. Outer sealing groove of the front end cover; 8. Cylinder block sealing ring; 9. Storage cylinder block; 10-a. First stator vane; 10-b. Second stator vane; 11-a. First stator sealing groove; 11-b. Second stator sealing groove; 12. Stator sealing piece; 13. Cylinder block positioning hole; 14. Cylinder block sealing groove; 15. Threaded hole; 16. Cylinder block rear end cover; 17. Outer sealing groove of the rear end cover; 18. Threaded through hole; 19. Screw; 20-a. Inner sealing groove of the front end cover; 20-b. Inner sealing groove of the rear end cover; 21-a. First shaft sealing ring; 21-b. Second shaft sealing ring; 21-c. Third shaft sealing ring; 21-d. Fourth shaft sealing ring; 22. Rotating shaft; 23-a. First rotor vane; 23-b. Second rotor vane; 24-a. First rotor sealing groove; 24-b. Second rotor sealing groove; 25. Rotor sealing piece; 26-a. First air cavity channel; 26-b. Second air cavity channel; 27-a. First rotating shaft sealing groove; 27-b. Second rotating shaft sealing groove; 27-c. Third rotating shaft sealing groove; 27-d. Fourth rotating shaft sealing groove; 28-a. First ball bearing; 28-b. Second ball bearing; 29-a. First gasket groove; 29-b. Second gasket groove; 30. Limit gasket; 31-a. First keyway; 31-b. Second keyway. Detailed implementation mode

[0063] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a 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 those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0064] In the description of the present invention, it should be understood that the terms "upper", "middle", "outer", "inner", etc. indicating the orientation or position relationship are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the components or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus cannot be understood as a limitation to the present invention.

[0065] Please refer to Figures 1 - 10As shown in the figure, the present invention is a gas-driven double-vane rotary oscillating motor, including a rotating shaft 22, a gas storage cylinder block 9, a cylinder front end cover 1 and a cylinder rear end cover 16. On the inner wall of the gas storage cylinder block 9, a first stator vane 10-a and a second stator vane 10-b are symmetrically arranged. The first stator vane 10-a, the second stator vane 10-b and the gas storage cylinder block 9 are of an integral structure. On the side of the first stator vane 10-a and the second stator vane 10-b away from the inner wall of the gas storage cylinder block 9, a first stator seal groove 11-a and a second stator seal groove 11-b are respectively provided. Between the rotating shaft 22 and the first stator seal groove 11-a and the second stator seal groove 11-b, stator seal sheets 12 are arranged;

[0066] On both sides of the rotating shaft 22, a first rotor vane 23-a and a second rotor vane 23-b are symmetrically arranged. The first rotor vane 23-a, the second rotor vane 23-b and the rotating shaft 22 are of an integral structure. On the side of the first rotor vane 23-a and the second rotor vane 23-b away from the rotating shaft 22, a first rotor seal groove 24-a and a second rotor seal groove 24-b are respectively provided. Between the inner wall of the gas storage cylinder block 9 and the first rotor seal groove 24-a and the second rotor seal groove 24-b, rotor seal sheets 25 are arranged. Through the rotor seal sheets 25, the sealing performance between the gas storage cylinder block 9 and the rotating shaft 22 is ensured. The rotating shaft 22 is installed inside the gas storage cylinder block 9, and the first stator vane 10-a, the second stator vane 10-b, the first rotor vane 23-a and the second rotor vane 23-b are arranged in a cross manner.

[0067] In the above structure, the rotating shaft 22 is supported and fixed inside the gas storage cylinder block 9 by the first rotor vane 23-a, the second rotor vane 23-b, the cylinder front end cover 1 and the cylinder rear end cover 16. One side of the rotating shaft 22 on the cylinder front end cover 1 can be welded to the sleeve and the rest of the external shaft, and the cylinder rear end cover 16 can be welded to the rest of the external shaft.

[0068] At both ends of the gas storage cylinder block 9, cylinder seal grooves 14 are provided. On the side of the middle protrusion of the cylinder front end cover 1, a front end cover outer seal groove 7 is provided. The cylinder seal groove 14 close to the cylinder front end cover 1 and the front end cover outer seal groove 7 cooperate with each other. On the side of the middle protrusion of the cylinder rear end cover 16, a rear end cover outer seal groove 17 is provided. The cylinder seal groove 14 close to the cylinder rear end cover 16 and the rear end cover outer seal groove 17 cooperate with each other. Between the cylinder seal grooves 14 on both sides and the front end cover outer seal groove 7 and the rear end cover outer seal groove 17, cylinder seal rings 8 are arranged. Through the cylinder seal rings 8, the sealing performance between the cylinder front end cover 1 and the cylinder rear end cover 16 and the gas storage cylinder block 9 is ensured.

[0069] A first intake hole 2-a, a second intake hole 2-b, a first exhaust hole 2-c and a second exhaust hole 2-d are penetrated and opened on the front end cover 1 of the cylinder block. Inside the air storage cylinder block 9, a first air pressure chamber 3-a, a second air pressure chamber 3-b, a third air pressure chamber 3-c and a fourth air pressure chamber 3-d are sequentially arranged. The first air pressure chamber 3-a, the second air pressure chamber 3-b, the third air pressure chamber 3-c and the fourth air pressure chamber 3-d are separated by a first stator vane 10-a, a second stator vane 10-b, a first rotor vane 23-a and a second rotor vane 23-b. The first intake hole 2-a corresponds to the first air pressure chamber 3-a, the second intake hole 2-b corresponds to the second air pressure chamber 3-b, the first exhaust hole 2-c corresponds to the third air pressure chamber 3-c, and the second exhaust hole 2-d corresponds to the fourth air pressure chamber 3-d. A gas plug interface 4 is threadedly arranged at the outer end of each of the first intake hole 2-a, the second intake hole 2-b, the first exhaust hole 2-c and the second exhaust hole 2-d.

[0070] A cylinder block positioning hole 13 for positioning and assembling the front end cover 1 of the cylinder block and the air storage cylinder block 9 is opened on one side of the first stator vane 10-a. A end cover positioning hole 5 is arranged on the front end cover 1 of the cylinder block. The end cover positioning hole 5 and the cylinder block positioning hole 13 cooperate with each other, and a positioning pin 6 is arranged between the end cover positioning hole 5 and the cylinder block positioning hole 13. The positioning pin 6 facilitates connecting the end cover positioning hole 5 and the cylinder block positioning hole 13 together, thereby achieving the purpose of fixing the air storage cylinder block 9 and the front end cover 1 of the cylinder block together.

[0071] A plurality of threaded holes 15 for connecting the air storage cylinder block 9 and the rear end cover 16 of the cylinder block are opened at one end of the air storage cylinder block 9. The rear end cover 16 of the cylinder block is in interference fit with the air storage cylinder block 9. A plurality of threaded through holes 18 are opened on the protruding part of the rear end cover 16 of the cylinder block. The threaded holes 15 and the threaded through holes 18 correspond to each other and cooperate with each other, and a screw 19 is threadedly arranged between the threaded hole 15 and the corresponding threaded through hole 18. The screw 19 facilitates connecting the threaded hole 15 and the corresponding threaded through hole 18 together, thereby achieving the purpose of fixing the rear end cover 16 of the cylinder block and the air storage cylinder block 9 together.

[0072] On one side of the outer wall of the rotating shaft 22, a first rotating shaft sealing groove 27-a and a second rotating shaft sealing groove 27-b are provided. On the inner surface of the front end cover 1 of the cylinder block, two inner front end cover sealing grooves 20-a are provided. A first shaft sealing ring 21-a is arranged between the inner front end cover sealing groove 20-a and the first rotating shaft sealing groove 27-a. A second shaft sealing ring 21-b is arranged between the inner front end cover sealing groove 20-a and the second rotating shaft sealing groove 27-b. The sealing performance between the front end cover 1 of the cylinder block and the rotating shaft 22 is ensured by the first shaft sealing ring 21-a and the second shaft sealing ring 21-b. On the other side of the outer wall of the rotating shaft 22, a third rotating shaft sealing groove 27-c and a fourth rotating shaft sealing groove 27-d are provided. On the inner surface of the rear end cover 16 of the cylinder block, two inner rear end cover sealing grooves 20-b are provided. A third shaft sealing ring 21-c is arranged between the inner rear end cover sealing groove 20-b and the third rotating shaft sealing groove 27-c. A fourth shaft sealing ring 21-d is arranged between the inner rear end cover sealing groove 20-b and the fourth rotating shaft sealing groove 27-d. The sealing performance between the rear end cover 16 of the cylinder block and the rotating shaft 22 is ensured by the third shaft sealing ring 21-c and the fourth shaft sealing ring 21-d.

[0073] On one side surface of the first rotor blade 23-a, a first air cavity channel 26-a is provided. The first air cavity channel 26-a penetrates to the other side of the second rotor blade 23-b. On the other side surface of the first rotor blade 23 away from the first air cavity channel 26-a, a second air cavity channel 26-b is provided. The second air cavity channel 26-b penetrates to the other side of the second rotor blade 23-b. Both the first air cavity channel 26-a and the second air cavity channel 26-b are inclined structures. The first air cavity channel 26-a and the second air cavity channel 26-b are located at the intersection position of two different cross-sections of the rotating shaft 22. Both ends of the first air cavity channel 26-a are respectively communicated with the first air pressure chamber 3-a and the fourth air pressure chamber 3-d. Through the first air cavity channel 26-a, a communication structure is formed between the diagonal first air pressure chamber 3-a and the fourth air pressure chamber 3-d, so that the air pressures inside the first air pressure chamber 3-a and the fourth air pressure chamber 3-d are the same. Both ends of the second air cavity channel 26-b are respectively communicated with the second air pressure chamber 3-b and the third air pressure chamber 3-c. Through the second air cavity channel 26-b, a communication structure is formed between the diagonal second air pressure chamber 3-b and the third air pressure chamber 3-c, so that the air pressures inside the second air pressure chamber 3-b and the third air pressure chamber 3-c are the same.

[0074] At positions near both ends of the rotating shaft 22, a first keyway 31-a and a second keyway 31-b are respectively provided. On both sides of the outer wall of the rotating shaft 22, a first ball bearing 28-a and a second ball bearing 28-b are respectively installed. The first ball bearing 28-a is arranged between the rotating shaft 22 and the front end cover 1 of the cylinder block, and the second ball bearing 28-b is arranged between the rotating shaft 22 and the rear end cover 16 of the cylinder block. Through the first ball bearing 28-a, the relative rotation between the rotating shaft 22 and the front end cover 1 of the cylinder block is ensured. At the same time, through the second ball bearing 28-b, the relative rotation between the rotating shaft 22 and the rear end cover 16 of the cylinder block is ensured. On one side of the surface of the rotating shaft 22 near the first keyway 31-a, a first gasket groove 29-a is provided. On one side of the surface of the rotating shaft 22 near the second keyway 31-b, a second gasket groove 29-b is provided. Limit gaskets 30 are arranged in both the first gasket groove 29-a and the second gasket groove 29-b. The two limit gaskets 30 cooperate with the first ball bearing 28-a and the second ball bearing 28-b respectively. Through the limit gaskets 30, it is convenient to limit and fix the first ball bearing 28-a and the second ball bearing 28-b. The first shaft seal ring 21-a, the second shaft seal ring 21-b, the third shaft seal ring 21-c, the fourth shaft seal ring 21-d, the cylinder block seal ring 8, the rotor sealing piece 25, and the stator sealing piece 12 are all made of polytetrafluoroethylene material.

[0075] A method for using a gas-driven double-vane rotary oscillating motor includes the following steps:

[0076] Step 1: Calculate the volume change of a single chamber. First, obtain the corresponding parameters. Ignoring the thicknesses of the first rotor blade 23-a, the second rotor blade 23-b, the first stator blade 10-a, and the second stator blade 10-b in the present invention, the inside of the storage cylinder block 9 is divided into four chambers, namely a first air pressure chamber 3-a, a second air pressure chamber 3-b, a third air pressure chamber 3-c, and a fourth air pressure chamber 3-d, by the cross-set first rotor blade 23-a, second rotor blade 23-b, first stator blade 10-a, and second stator blade 10-b. Therefore, the initial volume of a single chamber is:

[0077]

[0078] R: Inner radius of the cylinder block (R = D / 2, D is the inner diameter of the cylinder block);

[0079] r: Radius of the output shaft (r = d / 2, d is the diameter of the output shaft).

[0080] The volume change ΔV of a single chamber should be:

[0081] ΔV = arc length · H · L = R eff ·θ·H·L

[0082] Where:

[0083] H = R - r is the blade height;

[0084] L is the axial length of the cylinder block;

[0085] θ is the swing angle of the rotor blade;

[0086] R eff is the distance from the pressure center to the rotation axis

[0087] Step 2: Calculate the pressure difference and torque. Based on the volume change ΔV, the pressures in the high-pressure chamber and the low-pressure chamber are respectively:

[0088]

[0089] The effective pressure difference is:

[0090]

[0091] The torque formula is:

[0092] T(θ) = η·ΔP(θ)·A·R eff

[0093] Wherein, the effective acting area of the blade A = H·L;

[0094] η is the mechanical efficiency after losses caused by gas seal leakage, etc.;

[0095] V0 is the initial single-chamber volume;

[0096] P0 is the initial single-chamber pressure;

[0097] The final torque formula

[0098]

[0099] Where T friction is the frictional torque generated by the rotation of the rotor blade;

[0100] Step 3: According to the required reciprocating swing angle, combined with the calculated actual output torque, match the corresponding air pressure.

[0101] Example 1:

[0102] During use, assume that the first pneumatic chamber 3-a is clockwise facing the second pneumatic chamber 3-b. If it is required to rotate and swing clockwise, first, the inflation device fills the first pneumatic chamber 3-a with high-pressure gas through the first air inlet hole 2-a. At the same time, since the fourth pneumatic chamber 3-d and the first pneumatic chamber 3-a are connected through the first air chamber channel 26-a, the high-pressure gas filled into the first pneumatic chamber 3-a will also be filled into the fourth pneumatic chamber 3-d, so that the air pressures of the first pneumatic chamber 3-a and the fourth pneumatic chamber 3-d are the same;

[0103] Among them, the deflation device extracts the high-pressure gas in the third pneumatic chamber 3-c through the first exhaust hole 2-c. At the same time, since the second pneumatic chamber 3-b and the third pneumatic chamber 3-c are connected through the second air chamber channel 26-b, when extracting the high-pressure gas in the third pneumatic chamber 3-c, the high-pressure gas in the second pneumatic chamber 3-b will also be extracted, so that the air pressures of the second pneumatic chamber 3-b and the third pneumatic chamber 3-c are the same;

[0104] At this time, due to the different gas pressures of the adjacent first pneumatic chamber 3-a and the second pneumatic chamber 3-b, and the third pneumatic chamber 3-c and the fourth pneumatic chamber 3-d, the first rotor blade 23-a and the second rotor blade 23-b rotate. And because the air pressure of the first pneumatic chamber 3-a is greater than that of the second pneumatic chamber 3-b, and the air pressure of the fourth pneumatic chamber 3-d is greater than that of the third pneumatic chamber 3-c, the first rotor blade 23-a and the second rotor blade 23-b produce a clockwise rotational swing, thereby driving the rotating shaft 22 to rotate clockwise;

[0105] When counterclockwise rotation is required, only the opposite operation is needed. For example, deflate the fourth pneumatic chamber 3-d and inflate the second pneumatic chamber 3-b, so as to change the pressure between the adjacent chambers of the first pneumatic chamber 3-a, the second pneumatic chamber 3-b, the third pneumatic chamber 3-c, and the fourth pneumatic chamber 3-d, thereby driving the first rotor blade 23-a and the second rotor blade 23-b to perform a counterclockwise rotational swing, making the rotating shaft 22 rotate counterclockwise;

[0106] When different torques need to be generated to cope with different environments, just control the gas density and volume of the inflow and outflow gases to achieve the purpose of generating different torques.

[0107] Embodiment 2:

[0108] A gas-driven double-vane rotary oscillating motor in the present invention can be used as a driving source for an active stabilizer bar. The rotating shaft 22 on one side of the front end cover 1 of the cylinder block in the present invention is welded and connected to the active stabilizer half-bar through a sleeve, and the rear end cover 16 of the cylinder block is welded and connected to another stabilizer half-bar. At this time, an active stabilizer bar driven by gas is formed. At this time, the rotating shaft 22 connected to one side of the front end cover 1 of the cylinder block is the left half-bar of the active stabilizer bar, and the rotating shaft 22 connected to one side of the rear end cover 16 of the cylinder block is the right half-bar of the active stabilizer bar;

[0109] Fix the left half-bar and the right half-bar of the active stabilizer bar on the vehicle suspension respectively. When the vehicle body rolls to the left, the body sensor transmits a signal to the active stabilizer bar. The present invention decides to increase the high-pressure gas in the second air inlet hole 2-b and reduce the high-pressure gas in the second air outlet hole 2-d according to this signal. At this moment, the pressures in the second air pressure chamber 3-b and the third air pressure chamber 3-c are respectively greater than the pressures in the first air pressure chamber 3-a and the fourth air pressure chamber 3-d, so that the first rotor blade 23-a and the second rotor blade 23-b drive the rotating shaft 22 to rotate counterclockwise, and cause the active stabilizer half-bar to generate a torque rotating counterclockwise, thereby generating an upward acting force on the vehicle body that rolls to the left to prevent the vehicle body from rolling to the left;

[0110] Among them, the right half-bar of the active stabilizer bar generates a reaction force on the right side of the vehicle body due to the active force generated by the left half-bar. The two stabilizer half-bars prevent the vehicle body from rolling through the above process. Similarly, when the vehicle body rolls to the right, the present invention only needs to perform the opposite operation to the above process. When the present invention is used as the power source of the active stabilizer bar, it can prevent the vehicle body from rolling and ensure the smoothness and driving performance of the vehicle body;

[0111] At the same time, using the present invention as the power source is more simple and compact in structure compared with the stabilizer bar using a motor and a reducer structure, reducing the manufacturing cost. At the same time, compared with the air spring as the active stabilizer bar, the present invention only needs to use one to achieve the effect of two symmetrically installed air springs, greatly saving the application space of the vehicle body.

[0112] Therefore, the gas-driven double-vane rotary oscillating motor with the above structure in the present invention mainly fixes the rotating shaft 22 in the air storage cylinder block 9 through the front end cover 1 of the cylinder block and the rear end cover 16 of the cylinder block, and at the same time fills high-pressure gas through the first air inlet hole 2-a, the second air inlet hole 2-b, the first air outlet hole 2-c and the second air outlet hole 2-d, so that different air pressures are filled in the first air pressure chamber 3-a, the second air pressure chamber 3-b, the third air pressure chamber 3-c and the fourth air pressure chamber 3-d in the air storage cylinder block 9, thereby driving the first rotor blade 23-a and the second rotor blade 23-b to swing, and then driving the rotation of the rotating shaft 22, so as to achieve the purpose of pneumatic drive rotation and swing;

[0113] The sealing rings 21-a for the first shaft, 21-b for the second shaft, 21-c for the third shaft, 21-d for the fourth shaft, the cylinder block sealing ring 8, the rotor sealing piece 25, and the stator sealing piece 12 ensure the internal sealing of the device, avoiding air leakage, and thus can effectively improve the utilization efficiency of the gas.

[0114] The gas-driven double-vane rotary oscillating motor has a simple and compact structure and is easy to manufacture. By utilizing air pressure, a large torque can be provided. The rotating shaft 22 on one side of the front end cover 1 of the cylinder block can be welded to the other external shafts through a sleeve, and the rear end cover 16 of the cylinder block can be welded to the other external shafts, so that the present invention has a high adaptability and can be applied to various environments. At the same time, the utilization of gas reduces environmental pollution.

[0115] Example 3:

[0116] Assume that the inner diameter D of the gas storage cylinder block 9 is 100 mm and the diameter d of the rotating shaft 22 is 40 mm, then: R = 50 mm, r = 20 mm, H = 30 mm, R eff = 35 mm, L = 60 mm, the initial pressure P0 = 30 MPa, and the mechanical efficiency η = 0.8;

[0117] Initial single-chamber volume:

[0118]

[0119] Assume T friction = 20 N·m;

[0120] Torque when the swing angle θ = 0.1 rad (about 5.7°):

[0121]

[0122] The purpose of calculating the actual output torque of the motor according to the required swing angle is realized, and then the operation of the gas charging device and the gas discharging device is controlled to match the corresponding air pressure, which can meet different usage conditions, achieve the purpose of high-precision reciprocating swing, effectively improve the applicable range and usage effect of the motor, and at the same time effectively solve the disadvantages that the existing hydraulic drive system is prone to hydraulic oil leakage and cause environmental pollution after long-term use.

[0123] It should be further noted that the installation structure, connection method, or setting method of each component in the present invention are all common mechanical methods, and any implementation that can achieve its beneficial effects can be carried out.

[0124] In the description of this specification, the descriptions referring to the terms "one embodiment", "example", "specific example", etc. mean that the specific features, structures, materials or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0125] The preferred embodiments of the present invention disclosed above are only used to help explain the present invention. The preferred embodiments do not describe all the details in detail, nor do they limit the invention to the specific embodiments described. Obviously, many modifications and variations can be made according to the content of this specification. These embodiments are selected and specifically described in this specification to better explain the principles and practical applications of the present invention, so that those skilled in the art can understand and utilize the present invention well. The present invention is only limited by the claims and their full scope and equivalents.

Claims

1. A gas-driven double-vane rotary oscillating motor, comprising a rotating shaft (22), a gas storage cylinder block (9), a front cylinder head (1) and a rear cylinder head (16), characterized in that, On the inner wall of the storage cylinder block (9), a first stator blade (10-a) and a second stator blade (10-b) are symmetrically arranged. The first stator blade (10-a), the second stator blade (10-b) and the storage cylinder block (9) are of an integral structure. On the side of the first stator blade (10-a) and the second stator blade (10-b) away from the inner wall of the storage cylinder block (9), a first stator seal groove (11-a) and a second stator seal groove (11-b) are respectively formed. A stator seal piece (12) is arranged between the rotating shaft (22) and the first stator seal groove (11-a) and the second stator seal groove (11-b); On both sides of the rotating shaft (22), a first rotor blade (23-a) and a second rotor blade (23-b) are symmetrically arranged. The first rotor blade (23-a), the second rotor blade (23-b) and the rotating shaft (22) are of an integral structure. On the side of the first rotor blade (23-a) and the second rotor blade (23-b) away from the rotating shaft (22), a first rotor seal groove (24-a) and a second rotor seal groove (24-b) are respectively formed. A rotor seal piece (25) is arranged between the inner wall of the storage cylinder block (9) and the first rotor seal groove (24-a) and the second rotor seal groove (24-b). The rotating shaft (22) is installed inside the storage cylinder block (9), and the first stator blade (10-a), the second stator blade (10-b), the first rotor blade (23-a) and the second rotor blade (23-b) are arranged in a crossed manner.

2. The gas-driven double-vane rotary oscillating motor according to claim 1, characterized in that, At both ends of the storage cylinder block (9), cylinder block seal grooves (14) are provided. On one side of the middle protrusion of the cylinder front end cover (1), a front end cover outer seal groove (7) is provided. The cylinder block seal groove (14) near the cylinder front end cover (1) cooperates with the front end cover outer seal groove (7). On one side of the middle protrusion of the cylinder rear end cover (16), a rear end cover outer seal groove (17) is provided. The cylinder block seal groove (14) near the cylinder rear end cover (16) cooperates with the rear end cover outer seal groove (17). Cylinder block seal rings (8) are arranged between the cylinder block seal grooves (14) on both sides and the front end cover outer seal groove (7) and the rear end cover outer seal groove (17).

3. A gas-driven double-vane rotary oscillating motor according to claim 2, wherein A first intake hole (2-a), a second intake hole (2-b), a first exhaust hole (2-c), and a second exhaust hole (2-d) are penetratingly formed in the front end cover (1) of the cylinder block. Inside the storage cylinder block (9), a first air pressure chamber (3-a), a second air pressure chamber (3-b), a third air pressure chamber (3-c), and a fourth air pressure chamber (3-d) are sequentially arranged. The first air pressure chamber (3-a), the second air pressure chamber (3-b), the third air pressure chamber (3-c), and the fourth air pressure chamber (3-d) are separated by a first stator vane (10-a), a second stator vane (10-b), a first rotor vane (23-a), and a second rotor vane (23-b). The first intake hole (2-a) corresponds to the first air pressure chamber (3-a), the second intake hole (2-b) corresponds to the second air pressure chamber (3-b), the first exhaust hole (2-c) corresponds to the third air pressure chamber (3-c), and the second exhaust hole (2-d) corresponds to the fourth air pressure chamber (3-d). A gas plug interface (4) is threadedly provided at the outer end of each of the first intake hole (2-a), the second intake hole (2-b), the first exhaust hole (2-c), and the second exhaust hole (2-d).

4. A gas-driven double-vane rotary oscillating motor according to claim 3, characterized in that, A cylinder block positioning hole (13) for positioning and assembling the front end cover (1) of the cylinder block and the storage cylinder block (9) is formed on one side of the first stator vane (10-a). A end cover positioning hole (5) is provided on the front end cover (1) of the cylinder block. The end cover positioning hole (5) cooperates with the cylinder block positioning hole (13), and a positioning pin (6) is provided between the end cover positioning hole (5) and the cylinder block positioning hole (13).

5. A gas-driven double-vane rotary oscillating motor according to claim 4, characterized in that, A plurality of threaded holes (15) for connecting the storage cylinder block (9) and the rear end cover (16) of the cylinder block are formed at one end of the storage cylinder block (9). The rear end cover (16) of the cylinder block is in interference fit with the storage cylinder block (9). A plurality of threaded through holes (18) are formed in the protruding portion of the rear end cover (16) of the cylinder block. The threaded holes (15) correspond to and cooperate with the threaded through holes (18) one by one, and a screw (19) is threadedly provided between the threaded hole (15) and the corresponding threaded through hole (18).

6. A gas-driven double-vane rotary oscillating motor according to claim 5, characterized in that, On one side of the outer wall of the rotating shaft (22), a first rotating shaft sealing groove (27-a) and a second rotating shaft sealing groove (27-b) are provided. On the inner surface of the front end cover (1) of the cylinder block, two inner front end cover sealing grooves (20-a) are provided. A first shaft sealing ring (21-a) is provided between the inner front end cover sealing groove (20-a) and the first rotating shaft sealing groove (27-a). A second shaft sealing ring (21-b) is provided between the inner front end cover sealing groove (20-a) and the second rotating shaft sealing groove (27-b). On the other side of the outer wall of the rotating shaft (22), a third rotating shaft sealing groove (27-c) and a fourth rotating shaft sealing groove (27-d) are provided. On the inner surface of the rear end cover (16) of the cylinder block, two inner rear end cover sealing grooves (20-b) are provided. A third shaft sealing ring (21-c) is provided between the inner rear end cover sealing groove (20-b) and the third rotating shaft sealing groove (27-c). A fourth shaft sealing ring (21-d) is provided between the inner rear end cover sealing groove (20-b) and the fourth rotating shaft sealing groove (27-d).

7. A gas-driven double-vane rotary oscillating motor according to claim 6, characterized in that, On one side surface of the first rotor blade (23-a), a first air cavity channel (26-a) is provided, and the first air cavity channel (26-a) penetrates to the other side of the second rotor blade (23-b). On the other side surface of the first rotor blade (23) away from the first air cavity channel (26-a), a second air cavity channel (26-b) is provided, and the second air cavity channel (26-b) penetrates to the other side of the second rotor blade (23-b). Both the first air cavity channel (26-a) and the second air cavity channel (26-b) are inclined structures. The first air cavity channel (26-a) and the second air cavity channel (26-b) are located at the intersection position of two different cross-sections of the rotating shaft (22). Both ends of the first air cavity channel (26-a) are respectively communicated with the first air pressure chamber (3-a) and the fourth air pressure chamber (3-d). Both ends of the second air cavity channel (26-b) are respectively communicated with the second air pressure chamber (3-b) and the third air pressure chamber (3-c).

8. A gas-driven double-vane rotary oscillating motor according to claim 7, characterized in that, At positions near both ends of the rotating shaft (22), a first keyway (31-a) and a second keyway (31-b) are respectively provided. On both sides of the outer wall of the rotating shaft (22), a first ball bearing (28-a) and a second ball bearing (28-b) are respectively installed. The first ball bearing (28-a) is provided between the rotating shaft (22) and the front end cover (1) of the cylinder block. The second ball bearing (28-b) is provided between the rotating shaft (22) and the rear end cover (16) of the cylinder block.

9. A gas-driven double-vane rotary oscillating motor according to claim 8, characterized in that, On one side of the surface of the rotating shaft (22) close to the first keyway (31-a), a first gasket groove (29-a) is provided. On one side of the surface of the rotating shaft (22) close to the second keyway (31-b), a second gasket groove (29-b) is provided. Limit gaskets (30) are provided in both the first gasket groove (29-a) and the second gasket groove (29-b). The two limit gaskets (30) cooperate with the first ball bearing (28-a) and the second ball bearing (28-b) respectively. The first shaft seal ring (21-a), the second shaft seal ring (21-b), the third shaft seal ring (21-c), the fourth shaft seal ring (21-d), the cylinder block seal ring (8), the rotor sealing piece (25), and the stator sealing piece (12) are all made of polytetrafluoroethylene material.

10. The usage method of a gas-driven double-vane rotary oscillating motor according to claims 1-9, characterized in that, It includes the following steps: Step 1: Calculate the volume change of a single chamber. First, obtain the corresponding parameters. The initial volume of a single chamber of the first pneumatic chamber (3-a), the second pneumatic chamber (3-b), the third pneumatic chamber (3-c), and the fourth pneumatic chamber (3-d) is: R: Inner radius of the cylinder body (R = D / 2, D is the inner diameter of the cylinder body); r: Radius of the output shaft (r = d / 2, d is the diameter of the output shaft). The volume change ΔV of a single chamber should be: ΔV = Arc length · H · L = R eff · θ · H · L Where: H = R - r is the blade height; L is the axial length of the cylinder body; θ is the swing angle of the rotor blade; R eff is the distance from the center of pressure to the axis of rotation Step 2: Calculate the pressure difference and torque. Based on the volume change ΔV, the pressures of the high-pressure chamber and the low-pressure chamber are respectively: The effective pressure difference is: The torque formula is: T(θ) = η·ΔP(θ)·A·R eff Where the effective acting area of the blade A = H·L; η is the mechanical efficiency after losses caused by gas seal leakage, etc.; V0 is the initial single-chamber volume; P0 is the initial single-chamber pressure; The final torque formula where T friction is the frictional torque generated by the rotation of the rotor blade; Step 3: According to the required reciprocating swing angle, combine with the calculated actual output torque to match the corresponding air pressure.

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