Swing cylinder suitable for high-frequency working condition
By adopting the design of hydrostatic bearing and gap seal in the swing cylinder, the problem of wear and friction resistance of the swing cylinder under high-frequency working conditions is solved, and the performance and durability are improved.
Patent Information
- Application Number
- CN202420559491.2
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2024-03-21
- Publication Date
- 2025-01-24
- Estimated Expiration
- 2034-03-21
AI Technical Summary
The existing swing cylinders have problems such as rolling bearing wear caused by high-frequency reciprocating and swinging conditions, which are difficult to meet the needs of high-frequency operating conditions.
Use hydrostatic bearings instead of metal bearings to improve resistance to unbalanced forces and eccentric wear caused by wear; use gap seals instead of packing seals to reduce frictional resistance and extend product life.
Through the design of static pressure bearing and gap sealing, the friction is reduced, the performance and durability of the swinging cylinder are improved, and it is suitable for high -frequency operating conditions.
Smart Images
Figure CN222391671U_ABST
Abstract
Description
Technical Field
[0001] The utility model relates to the technical field of swing cylinders, in particular to a swing cylinder suitable for high-frequency working conditions. Background Art
[0002] For working conditions that require reciprocating swing, a swing cylinder is usually selected as the driving component. The output shaft of the swing cylinder can directly drive the load to swing back and forth. The existing swing cylinders are mainly spiral swing cylinders and gear rack swing cylinders. For some working conditions that require high-frequency reciprocating swing, these two types of swing cylinders cannot meet the use requirements. Therefore, for high-frequency working conditions, a blade swing cylinder is usually selected. However, the existing blade swing cylinder has the following disadvantages:
[0003] (1) When the swing cylinder is running, under the condition of partial load, the eccentricity of the output shaft cannot be avoided, and the wear problem of the rolling bearing cannot be ignored. After the rolling bearing is worn, it will cause unilateral metal contact between the stator and the rotor, thereby causing the gap leakage to increase and the volume ratio to decrease, which will have an adverse effect on the control.
[0004] (2) Most of the existing blade-type swing cylinders use packing seals. In high-frequency reciprocating swing, the seal material wears quickly and the product life is short. High-frequency operation causes the temperature of the swing cylinder to rise, which easily causes the seal to age and cannot meet the fatigue test conditions. The packing seal will generate a large friction resistance when the swing cylinder is working. This friction resistance is a multi-value nonlinear load and has a great impact on the performance of the swing cylinder. Utility Model Content
[0005] In order to solve the shortcomings existing in the prior art, the utility model provides a swing cylinder suitable for high-frequency working conditions, adopts hydrostatic bearings instead of metal bearings to improve the resistance to unbalanced force and eccentric wear caused by wear of metal bearings; adopts gap seals instead of packing seals to improve the wear problem of the sealing material of the swing cylinder.
[0006] The technical solution adopted by the utility model to solve its technical problems is: a swing cylinder suitable for high-frequency working conditions, comprising: a cylinder body, a front end cover, a rear end cover and an output shaft, the front end cover and the rear end cover are respectively connected to the front end and the rear end of the cylinder body, the output shaft is installed in the cylinder body, and the front and rear ends of the output shaft respectively pass through the front end cover and the rear end cover; wherein, a static pressure oil inlet port and a static pressure oil return port are provided on the cylinder body, and a static pressure oil inlet channel and a static pressure oil return channel are provided on the front end cover and the rear end cover, the static pressure oil inlet channel is connected to the static pressure oil inlet port, and the static pressure oil return channel is connected to the static pressure oil return port.
[0007] Furthermore, a thrust static pressure cavity is formed at one end of the front cover and the rear cover close to the cylinder body, and the thrust static pressure cavity is connected to the static pressure oil inlet channel.
[0008] Furthermore, a centripetal static pressure cavity is provided on the inner peripheral wall of the front end cover and the rear end cover, and the centripetal static pressure cavity is connected with the static pressure oil inlet channel.
[0009] Furthermore, a thrust oil return cavity is provided on the inner peripheral walls of the front end cover and the rear end cover, and the thrust oil return cavity is connected with the static pressure oil return channel.
[0010] Furthermore, a centripetal oil return cavity is provided on the inner peripheral wall of the front end cover and the rear end cover, and the centripetal oil return cavity is connected with the static pressure oil return channel.
[0011] Furthermore, the output shaft is provided with a first blade and a second blade, the first blade and the second blade are centrally symmetrically arranged, and the output shaft is provided with a first channel and a second channel.
[0012] Furthermore, a first step portion and a second step portion are provided on the inner circumferential wall of the cylinder body, and the first step portion and the second step portion are arranged opposite to each other, wherein a first cavity is formed between the first blade and the first step portion, a second cavity is formed between the first blade and the second step portion, a third cavity is formed between the second blade and the second step portion, and a fourth cavity is formed between the second blade and the first step portion.
[0013] Furthermore, two ends of the first channel are communicated with the first cavity and the third cavity respectively, and two ends of the second channel are communicated with the second cavity and the fourth cavity respectively.
[0014] Furthermore, a forward oil passage and a reverse oil passage are provided on the cylinder body, the forward oil passage is communicated with the first chamber, and the reverse oil passage is communicated with the fourth chamber.
[0015] Furthermore, a gap seal is formed between the front end cover end face and the cylinder end face, a gap seal is formed between the rear end cover end face and the cylinder end face; and a gap seal is formed between the first blade and the second blade and the inner wall of the cylinder.
[0016] Furthermore, the size of the gap of the gap seal is 0.03 mm to 0.05 mm.
[0017] The beneficial effects of the utility model are:
[0018] The utility model is a swing cylinder suitable for high-frequency working conditions. Through structural improvement, a stable oil film is formed between the mating surfaces of the front end cover, the rear end cover and the cylinder body, and a stable oil film is formed between the mating surfaces of the front end cover, the rear end cover and the output shaft, and the oil film acts as a static pressure bearing. In this way, when the output shaft rotates, the output shaft is equivalent to a "floating" state, and there is no friction between the front and rear end covers and the output shaft, and the axial force and radial force can be withstood. By means of gap sealing, not only the problem of easy wear of the sealing ring can be improved, but also the friction when the output shaft rotates can be reduced, thereby improving the swing performance. The swing cylinder of the utility model is suitable for use under high-frequency swing conditions. BRIEF DESCRIPTION OF THE DRAWINGS
[0019] The utility model is further described below in conjunction with the accompanying drawings and embodiments.
[0020] Figure 1 It is a three-dimensional schematic diagram of the swing cylinder of the utility model which is suitable for high-frequency working conditions.
[0021] Figure 2 It is an axial cross-sectional view of the swing cylinder of the utility model which is suitable for high-frequency working conditions.
[0022] Figure 3 It is a structural schematic diagram of the static pressure oil inlet channel of the utility model.
[0023] Figure 4 It is a structural schematic diagram of the pressure-inlet and oil-return passage of the utility model.
[0024] Figure 5 It is a radial cross-sectional view of the swing cylinder of the utility model which is suitable for high-frequency working conditions.
[0025] In the figure: 1. cylinder body; 2. front end cover; 3. rear end cover; 4. output shaft; 5. thrust static pressure chamber; 6. centripetal static pressure chamber; 7. thrust oil return chamber; 8. centripetal oil return chamber; 9. first chamber; 10. second chamber; 11. third chamber; 12. fourth chamber; 13. U-shaped retaining ring; 14. dust ring; 15. flat key; 101. static pressure oil inlet port; 102. static pressure oil return port; 103. first step portion; 104. second step portion; 105. forward oil passage; 106. reverse oil passage; 131. first oil inlet branch; 132. second oil inlet branch; 133. third oil inlet branch; 141. first oil return branch; 142. second oil return branch; 143. third oil return branch; 401. first blade; 402. second blade; 403. first channel; 404. second channel. DETAILED DESCRIPTION
[0026] Now the utility model is further described in detail with reference to the accompanying drawings. These drawings are simplified schematic diagrams, which only illustrate the basic structure of the utility model in a schematic manner, and therefore only show the components related to the utility model.
[0027] In the description of the present utility model, it is necessary to understand that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate positions or positional relationships based on the positions or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present utility model and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present utility model. In addition, features defined as "first" and "second" may explicitly or implicitly include one or more of such features. In the description of the present utility model, unless otherwise specified, "multiple" means two or more.
[0028] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installation", "connection" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.
[0029] like Figures 1 to 5 As shown, the swing cylinder suitable for high-frequency working conditions of the utility model comprises: a cylinder body 1, a front cover 2, a rear cover 3 and an output shaft 4. The front cover 2 and the rear cover 3 are respectively connected to the front end and the rear end of the cylinder body 1. The output shaft 4 is installed in the cylinder body 1, and the front and rear ends of the output shaft 4 respectively penetrate the front cover 2 and the rear cover 3. Among them, a static pressure oil inlet port 101 and a static pressure oil return port 102 are provided on the cylinder body 1, and a static pressure oil inlet channel and a static pressure oil return channel are provided on the front cover 2 and the rear cover 3. The static pressure oil inlet channel is connected to the static pressure oil inlet port 101, and the static pressure oil return channel is connected to the static pressure oil return port 102.
[0030] After the hydraulic oil is introduced into the static pressure oil inlet port 101, the hydraulic oil can flow into the space between the front end cover 2 and the cylinder body 1, between the rear end cover 3 and the cylinder body 1, between the front end cover 2 and the output shaft 4, and between the rear end cover 3 and the output shaft 4 through the static pressure oil inlet channel, so that a stable oil film is formed between the mating surfaces of the front end cover 2, the rear end cover 3 and the cylinder body 1, and a stable oil film is formed between the mating surfaces of the front end cover 2, the rear end cover 3 and the output shaft 4, and the oil film acts as a static pressure bearing. In this way, when the output shaft 4 rotates, the output shaft 4 is equivalent to a "floating" state, and there is no friction between the front and rear end covers and the output shaft 4, and the axial force and radial force can be withstood.
[0031] Specifically, the static oil inlet passage includes: a first oil inlet branch channel 131, a second oil inlet branch channel 132 and a third oil inlet branch channel 133. The first oil inlet branch channel 131 and the third oil inlet branch channel 133 are both arranged along the axial direction of the output shaft 4, and the second oil inlet branch channel 132 is arranged along the radial direction of the output shaft 4. The first oil inlet branch channel 131 is connected to the static oil inlet port 101, the second oil inlet branch channel 132 is connected to the first oil inlet branch channel 131, and the third oil inlet branch channel 133 is connected to the second oil inlet branch channel 132. The static pressure oil return channel includes: a first oil return branch channel 141, a second oil return branch channel 142 and a third oil return branch channel 143. The second oil return branch channel 142 is arranged along the axial direction of the output shaft 4. The first oil return branch channel 141 and the third oil return branch channel 143 are both arranged along the radial direction of the output shaft 4. The second oil return branch channel 142 is connected to the static pressure oil return port 102, the second oil return branch channel 142 is connected to the first oil return branch channel 141, and the third oil return branch channel 143 is connected to the second oil return branch channel 142.
[0032] Specifically, a thrust static pressure chamber 5 is provided at one end of the front end cover 2 and the rear end cover 3 near the cylinder body 1, and the thrust static pressure chamber 5 is connected to the static pressure oil inlet channel. A thrust oil return chamber 7 is provided on the inner peripheral wall of the front end cover 2 and the rear end cover 3, and the thrust oil return chamber 7 is connected to the static pressure oil return channel. For example, the thrust static pressure chamber 5 is connected to the third oil inlet branch 133, and the thrust oil return chamber 7 is connected to the first oil return branch 141. A centripetal static pressure chamber 6 is provided on the inner peripheral wall of the front end cover 2 and the rear end cover 3, and the centripetal static pressure chamber 6 is connected to the static pressure oil inlet channel. A centripetal oil return chamber 8 is provided on the inner peripheral wall of the front end cover 2 and the rear end cover 3, and the centripetal oil return chamber 8 is connected to the static pressure oil return channel. For example, the centripetal static pressure chamber 6 is connected to the second oil inlet branch 132, and the centripetal oil return chamber 8 is connected to the third oil return branch 143.
[0033] When hydraulic oil is introduced into the static pressure oil inlet port 101, the hydraulic oil enters the centripetal static pressure chamber 6 through the first oil inlet branch channel 131 and the second oil inlet branch channel 132. The hydraulic oil in the centripetal static pressure chamber 6 can enter the centripetal oil return chamber 8 through the gap, and then flow to the static pressure oil return port 102 through the third oil return branch channel 143 and the second oil return branch channel 142, thereby forming a stable oil film between the output shaft 4 and the inner walls of the front and rear end covers.
[0034] When hydraulic oil is introduced into the static pressure oil inlet port 101, the hydraulic oil enters the thrust static pressure chamber 5 through the first oil inlet branch channel 131, the second oil inlet branch channel 132, and the third oil inlet branch channel 133. The hydraulic oil in the thrust static pressure chamber 5 can enter the thrust oil return chamber 7 through the gap, and then flow to the static pressure oil return port 102 through the first oil return branch channel 141 and the second oil return branch channel 142, thereby forming a stable oil film between the output shaft 4 and the end faces of the front and rear end covers.
[0035] Specifically, the output shaft 4 is provided with a first blade 401 and a second blade 402, which are centrally symmetrically arranged, and the output shaft 4 is provided with a first channel 403 and a second channel 404. The inner peripheral wall of the cylinder body 1 is provided with a first step portion 103 and a second step portion 104, which are arranged opposite to each other, wherein a first cavity 9 is formed between the first blade 401 and the first step portion 103, a second cavity 10 is formed between the first blade 401 and the second step portion 104, a third cavity 11 is formed between the second blade 402 and the second step portion 104, and a fourth cavity 12 is formed between the second blade 402 and the first step portion 103. The two ends of the first channel 403 are respectively connected to the first cavity 9 and the third cavity 11, and the two ends of the second channel 404 are respectively connected to the second cavity 10 and the fourth cavity 12. A forward oil passage 105 and a reverse oil passage 106 are provided on the cylinder body 1 . The forward oil passage 105 is communicated with the first chamber 9 , and the reverse oil passage 106 is communicated with the fourth chamber 12 .
[0036] When hydraulic oil is introduced into the forward oil passage 105, the hydraulic oil enters the first chamber 9 and enters the third chamber 11 through the first passage 403, thereby the hydraulic oil can push the first blade 401 and the second blade 402 to rotate clockwise. When hydraulic oil is introduced into the reverse oil passage 106, the hydraulic oil enters the fourth chamber 12 and enters the second chamber 10 through the second passage 404, thereby the hydraulic oil can push the first blade 401 and the second blade 402 to rotate counterclockwise.
[0037] It should be noted that a gap seal is formed between the end face of the front end cover 2 and the end face of the cylinder body 1, a gap seal is formed between the end face of the rear end cover 3 and the end face of the cylinder body 1, and a gap seal is formed between the first blade 401 and the second blade 402 and the inner wall of the cylinder body 1. The gap size of the gap seal is 0.03mm to 0.05mm. That is to say, in this embodiment, the front and rear end covers and the end face of the cylinder body 1, as well as the two blades and the inner wall of the cylinder body 1 are not sealed by a sealing ring, but a gap seal is formed by designing the gap size. Under high-frequency (e.g., 50Hz, 100Hz) swinging conditions, the hydraulic oil in the first chamber 9, the second chamber 10, the third chamber 11, and the fourth chamber 12 will not leak through such a small gap. Through the gap seal, not only can the problem of easy wear of the sealing ring be improved, but also the friction force when the output shaft 4 rotates can be reduced, thereby improving the swing performance.
[0038] In addition, a U-shaped retaining ring 13 and a dust ring 14 are embedded on the inner walls of the front cover 2 and the rear cover 3. The U-shaped retaining ring 13 is used to prevent the hydraulic oil inside the swing cylinder from leaking to the outside, and the dust ring 14 is used to prevent external dust from entering the swing cylinder. A flat key 15 is also provided on the output shaft 4 to facilitate connection with the load.
[0039] In summary, the utility model is suitable for the swing cylinder of high-frequency working conditions. After the hydraulic oil is introduced into the static pressure oil inlet port 101, the hydraulic oil can flow into the space between the front end cover 2 and the cylinder body 1, between the rear end cover 3 and the cylinder body 1, between the front end cover 2 and the output shaft 4, and between the rear end cover 3 and the output shaft 4 through the static pressure oil inlet channel, so that a stable oil film is formed between the mating surfaces of the front end cover 2, the rear end cover 3 and the cylinder body 1, and a stable oil film is formed between the mating surfaces of the front end cover 2, the rear end cover 3 and the output shaft 4, and the oil film acts as a static pressure bearing. In this way, when the output shaft 4 rotates, the output shaft 4 is equivalent to a "floating" state, and there is no friction between the front and rear end covers and the output shaft 4, and the axial force and radial force can be borne. By means of gap sealing, not only can the problem of easy wear of the sealing ring be improved, but also the friction when the output shaft 4 rotates can be reduced, and the swing performance can be improved. The swing cylinder of the utility model is suitable for use under high-frequency swing conditions.
[0040] Based on the above ideal embodiments of the utility model, the relevant staff can make various changes and modifications without departing from the technical concept of the utility model through the above description. The technical scope of the utility model is not limited to the content of the specification, and its technical scope must be determined according to the scope of the claims.
Claims
1. A swing cylinder suitable for high-frequency working conditions, characterized in that: include: A cylinder body (1), a front end cover (2), a rear end cover (3) and an output shaft (4), wherein the front end cover (2) and the rear end cover (3) are respectively connected to the front end and the rear end of the cylinder body (1), and the output shaft (4) is installed in the cylinder body (1), and the front and rear ends of the output shaft (4) respectively penetrate the front end cover (2) and the rear end cover (3); wherein: The cylinder body (1) is provided with a static pressure oil inlet port (101) and a static pressure oil return port (102); the front end cover (2) and the rear end cover (3) are both provided with a static pressure oil inlet passage and a static pressure oil return passage; the static pressure oil inlet passage is connected to the static pressure oil inlet port (101), and the static pressure oil return passage is connected to the static pressure oil return port (102).
2. The oscillating cylinder suitable for high-frequency working conditions according to claim 1, characterized in that: The front end cover (2) and the rear end cover (3) are both provided with a thrust static pressure chamber (5) at one end close to the cylinder body (1), and the thrust static pressure chamber (5) is connected to the static pressure oil inlet channel.
3. The swing cylinder suitable for high-frequency working conditions according to claim 1, characterized in that: A centripetal static pressure chamber (6) is provided on the inner peripheral walls of the front end cover (2) and the rear end cover (3), and the centripetal static pressure chamber (6) is connected to the static pressure oil inlet channel.
4. The swing cylinder suitable for high-frequency working conditions as claimed in claim 2, characterized in that: A thrust oil return chamber (7) is provided on the inner peripheral walls of the front end cover (2) and the rear end cover (3), and the thrust oil return chamber (7) is connected to the static pressure oil return channel.
5. The oscillating cylinder suitable for high-frequency working conditions as claimed in claim 3, characterized in that: A centripetal oil return chamber (8) is provided on the inner peripheral walls of the front end cover (2) and the rear end cover (3), and the centripetal oil return chamber (8) is connected to the static pressure oil return channel.
6. The swing cylinder suitable for high-frequency working conditions according to claim 1, characterized in that: The output shaft (4) is provided with a first blade (401) and a second blade (402), the first blade (401) and the second blade (402) are centrally symmetrically arranged, and the output shaft (4) is provided with a first channel (403) and a second channel (404).
7. The oscillating cylinder suitable for high-frequency working conditions according to claim 6, characterized in that: A first step portion (103) and a second step portion (104) are provided on the inner peripheral wall of the cylinder body (1), and the first step portion (103) and the second step portion (104) are arranged opposite to each other, wherein a first cavity (9) is formed between the first blade (401) and the first step portion (103), a second cavity (10) is formed between the first blade (401) and the second step portion (104), a third cavity (11) is formed between the second blade (402) and the second step portion (104), and a fourth cavity (12) is formed between the second blade (402) and the first step portion (103).
8. The oscillating cylinder suitable for high-frequency working conditions according to claim 7, characterized in that: The two ends of the first channel (403) are respectively connected to the first chamber (9) and the third chamber (11), and the two ends of the second channel (404) are respectively connected to the second chamber (10) and the fourth chamber (12).
9. The oscillating cylinder suitable for high-frequency working conditions according to claim 7, characterized in that: The cylinder body (1) is provided with a forward oil passage (105) and a reverse oil passage (106); the forward oil passage (105) is communicated with the first chamber (9), and the reverse oil passage (106) is communicated with the fourth chamber (12).
10. The oscillating cylinder suitable for high-frequency working conditions according to claim 6, characterized in that: A gap seal is formed between the end surface of the front end cover (2) and the end surface of the cylinder body (1), and a gap seal is formed between the end surface of the rear end cover (3) and the end surface of the cylinder body (1); and a gap seal is formed between the first blade (401) and the second blade (402) and the inner wall of the cylinder body (1).
11. The oscillating cylinder suitable for high-frequency working conditions according to claim 10, characterized in that: The size of the gap of the gap seal is 0.03 mm to 0.05 mm.