CN113653764A - Damping thrust bearing based on hydraulic servo control - Google Patents
Damping thrust bearing based on hydraulic servo control Download PDFInfo
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- CN113653764A CN113653764A CN202110850204.4A CN202110850204A CN113653764A CN 113653764 A CN113653764 A CN 113653764A CN 202110850204 A CN202110850204 A CN 202110850204A CN 113653764 A CN113653764 A CN 113653764A
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- 238000013016 damping Methods 0.000 title claims abstract description 75
- 238000006073 displacement reaction Methods 0.000 claims abstract description 69
- 238000003825 pressing Methods 0.000 claims abstract description 42
- 230000009467 reduction Effects 0.000 claims abstract description 31
- 230000008093 supporting effect Effects 0.000 claims abstract description 16
- 238000007789 sealing Methods 0.000 claims abstract description 13
- 238000013461 design Methods 0.000 claims abstract description 12
- 230000007704 transition Effects 0.000 claims description 9
- 230000001681 protective effect Effects 0.000 claims description 3
- 230000010354 integration Effects 0.000 claims description 2
- 238000002360 preparation method Methods 0.000 claims 1
- 239000003921 oil Substances 0.000 description 19
- 239000010720 hydraulic oil Substances 0.000 description 7
- 230000005540 biological transmission Effects 0.000 description 6
- 230000005284 excitation Effects 0.000 description 6
- 230000009471 action Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000008569 process Effects 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000005266 casting Methods 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000002955 isolation Methods 0.000 description 1
- 230000009191 jumping Effects 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012544 monitoring process Methods 0.000 description 1
- 239000004576 sand Substances 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/023—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means
- F16F15/027—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using fluid means comprising control arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/046—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means using combinations of springs of different kinds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
- F16F15/06—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means with metal springs
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- General Engineering & Computer Science (AREA)
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- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Support Of The Bearing (AREA)
Abstract
The invention relates to a vibration reduction thrust bearing based on hydraulic servo control, which comprises a thrust bearing body, a reversing sleeve ring, a reversing thrust block, a forward sleeve ring, a vibration reduction element, an integrated valve block and a control box, wherein the reversing sleeve ring is arranged on the thrust bearing body; the damping elements are uniformly arranged in the positive vehicle sleeve ring along the circumferential direction and comprise a hydraulic cylinder, a damping spring, a piston, a thrust supporting block, a spring pressing cap, a magnetic ring and a displacement sensor; all the vibration reduction elements are connected in parallel, oil inlets of the sealing cavities are connected with the integrated valve block after being connected through oil pipes, and the integrated valve block is connected with a hydraulic system; each displacement sensor is respectively connected with the control box, the integrated valve block is connected with the control box, and the control box controls the integrated valve block to act according to displacement signals of the displacement sensors so as to actuate hydraulic pressure, so that the displacement of the propulsion shaft system is kept within a design range. The self-adaptive shafting thrust is controlled through the hydraulic servo, the shafting displacement is ensured not to exceed the allowable displacement of the shafting longitudinal displacement, and the vibration reduction function is realized within the full thrust range.
Description
Technical Field
The invention belongs to the technical field of ship power devices, and particularly relates to a damping thrust bearing based on hydraulic servo control.
Background
The reduction of the transmission of the propeller longitudinal excitation to the hull is of great significance for the control of the vibration noise. Based on the vibration reduction and isolation idea, the vibration reduction function is integrated in the transmission path of the excitation force of the shafting propeller, the required rigidity value is reached through a vibration reduction element with reasonable design, and the transmission of the longitudinal excitation force of the propeller to the hull is effectively reduced. For example, the disc spring type vibration damping thrust bearing and other equipment, the disc spring type vibration damping thrust bearing reduces the longitudinal rigidity of the thrust bearing by arranging a disc spring vibration damping element in a non-rotating part in the thrust bearing, so that the purpose of transmitting the longitudinal excitation force of the isolated propeller to the hull is achieved, but the shafting can jump to the fore along with the increase of the propeller thrust after the rigidity is reduced and is limited by the allowable displacement of the shafting, the disc spring type vibration damping thrust bearing can be provided with a rigid limit protection structure to ensure that the jumping amount of the shafting is in the allowable displacement range, when the propeller thrust is too large, the disc spring type thrust bearing loses the vibration damping effect after the rigidity limit of the disc spring type thrust bearing, and therefore, the disc spring type vibration damping thrust bearing only has the vibration damping function in a certain thrust range.
Disclosure of Invention
The invention aims to solve the technical problem that the conventional vibration-damping thrust bearing or other shafting vibration-damping equipment only has a longitudinal vibration-damping function within a certain thrust range, and provides a vibration-damping thrust bearing based on hydraulic servo control.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a vibration reduction thrust bearing based on hydraulic servo control comprises a thrust bearing body, wherein the thrust bearing body comprises a thrust shaft, a thrust bearing shell, a reversing sleeve ring, a reversing thrust block, a forward thrust block and a forward sleeve ring which are arranged in the thrust bearing shell; the damping thrust bearing also comprises a damping element, an integrated valve block and a control box; the damping elements are uniformly arranged in the forward sleeve ring along the circumferential direction, and each damping element comprises a hydraulic cylinder, a damping spring, a piston, a thrust supporting block, a spring pressing cap, a magnetic ring and a displacement sensor; the rear end of the spring pressing cap is positioned in the hydraulic cylinder, the front end of the spring pressing cap extends out of the middle part of the front end of the hydraulic cylinder, the spring pressing cap can move axially relative to the hydraulic cylinder, the thrust supporting block is fixedly arranged at the front end of the spring pressing cap, and the thrust supporting block is in contact with the forward thrust block; the magnetic ring is fixedly arranged at the rear end of the spring pressing cap; the piston is arranged in the cylinder body, the damping spring is arranged between the spring pressing cap and the piston, and a sealing cavity is formed between the piston and the rear end of the hydraulic cylinder; the displacement sensor is fixedly arranged at the rear end of the hydraulic cylinder; the vibration reduction elements are connected in parallel, oil inlets of sealing cavities of the vibration reduction elements are connected with the integrated valve block after being connected through oil pipes, and an oil inlet and an oil return port of the integrated valve block are connected with a hydraulic system; the displacement sensors of the vibration reduction elements are respectively connected with the control box, the integrated valve block is connected with the control box, and the control box controls the integrated valve block to act according to displacement signals of the displacement sensors to actuate hydraulic pressure, so that the displacement of the propulsion shafting is kept within a design range.
In the above scheme, the hydraulic cylinder comprises a cylinder body, a front end cover and a rear end cover, wherein the front end cover and the rear end cover are fixedly arranged at two ends of the cylinder body.
In the above scheme, the vibration damping element further comprises a transition joint fixedly mounted at the rear end of the rear end cover, and the transition joint axially penetrates out of the thrust bearing housing so as to be connected with the integrated valve block.
In the scheme, the displacement sensor is a magnetostrictive displacement sensor, the displacement sensor is fixedly arranged on the rear end cover, and the body of the displacement sensor extends into the cylinder body; the vibration reduction element further comprises a sealing sleeve which is sleeved outside the sensor body and is fixedly connected with the rear end cover.
In the scheme, the outer diameter of the thrust supporting block is larger than the inner diameter of the front end cover, a protective gap is arranged between the thrust supporting block and the front end cover, and the thrust shafting displacement is not more than limited displacement.
In the scheme, a designed gap is reserved at the position where the spring pressing cap penetrates through the front end cover to prevent the spring pressing cap from being in rigid contact with the front end cover.
In the above scheme, the magnetic ring is fixedly installed at the rear end of the spring pressing cap through a magnetic ring fixing device, the magnetic ring fixing device comprises a magnetic ring fixing rod and a magnetic ring pressing plate, the magnetic ring fixing rod is fixedly installed at the rear end of the spring pressing cap, the magnetic ring pressing plate is fixedly installed at the rear end of the magnetic ring fixing rod, and the magnetic ring is embedded between the magnetic ring fixing rod and the magnetic ring pressing plate.
In the above scheme, the vibration reduction thrust bearing further comprises a backing adjustment plate and a forward adjustment plate, the backing adjustment plate is arranged between the thrust bearing shell and the backing lantern ring, and the forward adjustment plate is arranged between the thrust bearing shell and the forward lantern ring.
In the above scheme, the vibration reduction thrust bearing further comprises an upper support bearing bush and a lower support bearing bush, wherein the upper support bearing bush and the lower support bearing bush are arranged on the inner side of the turning sleeve ring to form radial support for the thrust shaft.
In the scheme, the control box comprises a display mode and a control mode, and when the control box is in the display mode, a hydraulic servo control system of the thrust bearing does not participate in the work; when the control box is in a 'control' mode, a hydraulic servo control system of the thrust bearing participates in work, and at the moment, the control box controls the integrated valve block to act according to a displacement signal of the displacement sensor to actuate hydraulic pressure, so that the displacement of the thrust shaft system is kept within a design range.
The invention has the beneficial effects that:
1. the damping thrust bearing based on hydraulic servo control provided by the invention is internally integrated with a damping element and has a longitudinal damping function; the damping function of the damping element is mainly realized by the damping spring, the rigidity of the damping spring can be designed according to the requirement of the actual damping frequency range, and the damping requirements under different frequencies are realized.
2. Because the ship propulsion system has certain design requirements on the longitudinal displacement of the shafting, the design value is generally not allowed to be exceeded. According to the idea, the vibration reduction element is also provided with a limit value, under the action of propeller thrust, when the longitudinal displacement of a shaft system exceeds a designed value, the magnetostrictive displacement sensor collects displacement signals and transmits the displacement signals to the control box, the control box sends out instructions according to a set program algorithm, hydraulic oil is injected into or discharged from a sealed cavity of the vibration reduction element through controlling the action of the integrated valve block, then the piston in the cylinder is activated to act, the vibration reduction spring moves towards the fore part or the aft part, and finally the position of the thrust shaft is adjusted to be within the range of the designed value. The whole process self-adaptation screw thrust avoids leading to shafting displacement transfinite because of thrust increase compression elasticity damping element to realize possessing the damping function in the full thrust scope.
3. The vibration reduction element is provided with rigid limit protection, rigid limit is realized under the condition that hydraulic control fails or special working conditions, the displacement of a protection shaft system does not exceed limited displacement, the supporting effect is ensured, and the vibration source is prevented from being damaged.
4. The novel vibration reduction thrust bearing provided by the invention is mainly used for transmitting thrust and torque, simultaneously reduces the transmission of propeller longitudinal vibration excitation to a ship body, integrates a longitudinal vibration reduction function inside, and controls the thrust of the self-adaptive shafting through a hydraulic servo so as to realize the vibration reduction function in the full thrust range, and is particularly suitable for shafting requiring a large vibration reduction range.
Drawings
The invention will be further described with reference to the accompanying drawings and examples, in which:
FIG. 1 is an overall block diagram of a damped thrust bearing based on hydraulic servo control according to the present invention;
FIG. 2 is a block diagram of a damping element of the damped thrust bearing of FIG. 1;
FIG. 3 is a schematic view of a control housing of the dampened thrust bearing shown in FIG. 1.
In the figure: 10. a thrust bearing body; 11. a thrust shaft; 111. a thrust ring; 121. an upper housing; 122. a lower housing; 131. a backing adjustment plate; 132. a vehicle correcting adjusting plate; 141. a reversing collar; 142. a turning collar; 151. a reversing thrust block; 152. a forward thrust block; 161. an upper support bearing shell; 162. a lower supporting bearing bush; 171. a reversing end face oil seal; 172. turning an end face oil seal;
20. a damping element; 21. a thrust support block; 22. a front end cover; 23. a spring pressing cap; 24. a cylinder body; 25. a damping spring; 26. a piston; 27. a sealing sleeve; 28. a rear end cap; 29. a displacement sensor; 210. a magnetic ring fixing rod; 211. a magnetic ring; 212. a magnetic ring pressing plate; 213. a transition joint;
30. an integration valve block;
40. and a control box.
Detailed Description
For a more clear understanding of the technical features, objects and effects of the present invention, embodiments of the present invention will now be described in detail with reference to the accompanying drawings.
As shown in fig. 1, a damping thrust bearing based on hydraulic servo control according to an embodiment of the present invention includes a thrust bearing body 10, a damping element 20, an integrated valve block 30, and a control box 40.
The thrust bearing body 10 includes a thrust shaft 11, a thrust bearing housing, a reverse adjustment plate 131, a reverse collar 141, a reverse thrust block 151, a forward thrust block 152, a forward collar 142, a forward adjustment plate 132, an upper support bearing bush 161, a lower support bearing bush 162, a reverse end face oil seal 171, and a forward end face oil seal 172. Wherein, the middle part of the thrust shaft 11 is a thrust ring 111; the reversing adjusting plate 131, the reversing sleeve ring 141, the reversing thrust block 151, the thrust ring 111, the forward thrust block 152, the forward sleeve ring 142 and the forward adjusting plate 132 are sequentially arranged along the axial direction and are jointly arranged in the thrust bearing shell; the upper support bearing bush 161 and the lower support bearing bush 162 are arranged on the inner side of the forward turning sleeve ring 142 to form radial support for the thrust shaft 11; further, in order to prevent leakage of oil inside the thrust bearing, a reverse end face oil seal 171 and a forward end face oil seal 172 are provided at both ends of the housing, respectively. The clearances between the reverse thrust block 151, the forward thrust block 152 and the thrust collar 111 are respectively realized by adjusting the thicknesses of the reverse adjustment plate 131 and the forward adjustment plate 132.
In this embodiment, eight reverse thrust blocks 151 and eight forward thrust blocks 152 are uniformly distributed along the circumferential direction of the shaft axis. Eight sets of damping elements 20 are also circumferentially disposed uniformly within the centering collar 142.
As shown in fig. 2, the damping element 20 includes a cylinder 24, a damping spring 25, a piston 26, a front end cap 22, a rear end cap 28, a thrust support block 21, a spring cap 23, a magnetic ring 211, a magnetic ring fixing device, a displacement sensor 29, and a sealing sleeve 27. The front end cover 22 and the rear end cover 28 are fixedly arranged at two ends of the cylinder body 24; the rear end of the spring pressing cap 23 is positioned in the cylinder body 24, the front end of the spring pressing cap extends out of the cylinder body 24 from the middle part of the front end cover 22, and the spring pressing cap 23 can move axially relative to the cylinder body 24; the thrust supporting block 21 is fixedly arranged at the front end of the spring pressing cap 23, and the thrust supporting block 21 is contacted with the forward driving thrust block 152; the magnetic ring 211 is fixedly arranged at the rear end of the spring pressing cap 23 through a magnetic ring fixing device, specifically, the magnetic ring fixing device comprises a magnetic ring fixing rod 210 and a magnetic ring pressing plate 212, the magnetic ring fixing rod 210 is fixedly arranged at the rear end of the spring pressing cap 23, the magnetic ring pressing plate 212 is fixedly arranged at the rear end of the magnetic ring fixing rod 210, and the magnetic ring 211 is embedded between the magnetic ring fixing rod 210 and the magnetic ring pressing plate 212; the displacement sensor 29 is a magnetostrictive displacement sensor, and a sensor body extends into the cylinder body 24 and is fixedly arranged on the rear end cover 28; the sealing sleeve 27 is sleeved outside the sensor body and is fixedly connected with the rear end cover 28; the piston 26 is arranged in the cylinder body 24, and the damping spring 25 is arranged between the spring pressing cap 23 and the piston 26; the piston 26 is provided with seal rings on the inner and outer peripheries thereof to form a sealed chamber with the cylinder 24, the seal sleeve 27, and the rear end cap 28. Damping element 20 further includes a transition joint 213 fixedly mounted to the aft end of aft end cover 28, transition joint 213 extending axially from the thrust bearing housing for connection to manifold block 30.
When the device works, the eight vibration reduction elements 20 are connected in parallel, oil inlets of respective transition joints 213 are connected by oil pipes and then connected with oil outlets of the integrated valve block 30, the oil inlets and the oil return ports of the integrated valve block 30 are connected into a hydraulic system, hydraulic oil with certain pressure is injected into or discharged out of a sealing cavity of the vibration reduction elements 20, self-balancing of the internal pressure of the vibration reduction elements 20 is achieved, when thrust is transmitted to the forward thrust block 152 through the thrust shaft 11 and then transmitted to the vibration reduction elements 20, the thrust is balanced with spring pressure and hydraulic oil pressure, and further, specific pressure balance of the eight forward thrust blocks 152 is achieved. The displacement sensor 29 signal wires of each vibration damping element 20 are respectively connected with the control box 40, so that the transmission and monitoring of the displacement signals of the thrust shaft are realized; the signal line of the integrated valve block 30 is connected with the control box 40, and the control box 40 controls the integrated valve block 30 to act according to the displacement signal of the displacement sensor 29 to actuate hydraulic pressure, so that the displacement of the propulsion shafting is ensured to be kept within a design range.
The control box 40 includes two operation modes of "display" and "control":
when the control box 40 is in the "show" mode, the hydraulic servo control system of the thrust bearing is not engaged. When the thrust shaft 11 bears the forward thrust, the thrust is transmitted to the ship shell through the thrust bearing base sequentially through the forward thrust block 152, the vibration reduction element 20, the forward adjusting plate 132 and the thrust bearing shell; when the thrust shaft 11 bears the reverse thrust, the thrust is transmitted to the ship shell through the thrust bearing base via the reverse thrust block 151, the reverse collar 141, the reverse adjustment plate 131 and the thrust bearing shell in sequence.
The control box 40 is in "control" mode, in which the hydraulic servo control system of the thrust bearing is engaged. Under the reverse working condition, the transmission path of the propeller thrust through the thrust bearing is completely the same as that in the display mode. However, in the normal operation, when the pushing force is transmitted to the damping element 20, the pushing force support block 21 will force the spring cap 23 to compress the damping spring 25, and the magnetic ring fixing rod 210, the magnetic ring 211 and the magnetic ring pressing plate 212 will also move to the bow along with the spring cap 23. At this time, the magnetostrictive displacement sensor 29 will acquire the actual position of the magnetic ring 211 and transmit this displacement signal to the control box 40. When the thrust force continues to increase, so that the longitudinal displacement of the thrust shaft 11 exceeds the design range, the control box 40 sends a control instruction to the integrated valve block 30 according to a displacement signal measured by the magnetostrictive displacement sensor 29 and a predetermined program algorithm, and then controls hydraulic oil to enter the hydraulic oil chamber of the vibration damping element 20 through the oil passages of the transition joint 213 and the rear end cover 28. When the pressure reaches a certain value, the piston 26 is pushed to move towards the stern under the action of hydraulic oil, so that the damping spring 25, the spring pressing cap 23 and the thrust supporting block 21 are driven to move towards the stern, finally, the longitudinal displacement of the thrust shaft falls into the designed value range again, the control box 40 sends out an instruction again at the moment, the integrated valve block 30 stops oil supply, and the thrust bearing has a damping function again. If the propeller thrust continues to increase, the working process of the intellectual achievement also can be changed. In the "control" mode of the control box 40, if the propeller thrust is reduced from a certain large value so that the longitudinal displacement of the thrust shaft 11 is lower than the design range, the hydraulic servo control system also participates in the work, the only difference is that the control box 40 sends an oil drainage instruction to the integrated valve block 30 at this time, and the final purpose is still to make the longitudinal displacement of the thrust shaft fall within the design range, and the working principle and the working process thereof are not repeated here.
As shown in fig. 3, the control panel of the control box 40 displays the hydraulic oil pressure, the displacement measurement value of the damping element 20, and the average value. The display and the control share one knob, when the knob points to the display, the control box 40 is in a display state, and at the moment, a hydraulic servo control system of the thrust bearing does not participate in the work; the knob pointing to "control" indicates that the control box 40 is in a control state. The "number toggle" button can sequentially toggle to view the displacement measurements of the damping elements 20. The "mute" button may mute the buzzer when the control box 40 is alarming.
Further preferably, the outer diameter of the thrust support block 21 is larger than the inner diameter of the front end cover 22, and a protective gap is arranged between the thrust support block 21 and the front end cover 22. When the thrust increasing speed is too fast or the hydraulic control fails, the thrust supporting block 21 is in rigid contact with the front end cover 22 under the action of excitation force, at the moment, the damping element 20 loses the damping function, but the damping element still can play a supporting and bearing role, and the displacement of a thrust shaft system is protected from exceeding the limited displacement. When the control box 40 is in the display working mode, the thrust bearing is only in the working condition of forward driving, and the propeller thrust does not enable the thrust support block 21 to be in contact with the front end cover 22, so that the thrust bearing has the vibration reduction function.
Further optimizing, a designed gap is reserved at the position where the spring pressing cap 23 penetrates through the front end cover 22, so that the spring pressing cap 23 is prevented from being in rigid contact with the front end cover 22, and the damping effect is prevented from being weakened by the rigid contact.
Further preferably, the spring pressing cap 23 and the piston 26 are both provided with skirts to effectively protect the damping spring 25 in the middle and prevent the damping spring 25 from deflecting.
Preferably, the rear end cover 28 is provided with an exhaust hole, and the position of the exhaust hole is adjusted according to the installation direction of the damping element 20, so that the exhaust hole is located at a physical high position and used for exhausting air in the sealing cavity during initial installation.
Further optimize, the thrust bearing casing includes casing 121 and casing 122 down, and casing 121 and casing 122 all adopt the welding piece down, avoid adopting casting process to cause the inside defects such as gas pocket, sand hole that exist of casing material, and the mould unloading is not needed in the welding simultaneously, can practice thrift the cost.
Further optimized, the damping function of the damping element 20 is realized mainly by means of the damping spring 25. The rigidity of the damping spring 25 can be designed as required, and the rigidity of the spiral spring is designed according to the actual damping frequency range requirement, so that the damping requirements under different frequencies are met.
In this embodiment, eight thrust blocks are listed as an example, and other numbers are still within the protection range.
While the present invention has been described with reference to the embodiments shown in the drawings, the present invention is not limited to the embodiments, which are illustrative and not restrictive, and it will be apparent to those skilled in the art that various changes and modifications can be made therein without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (10)
1. A damping thrust bearing based on hydraulic servo control comprises a thrust bearing body (10), wherein the thrust bearing body (10) comprises a thrust shaft (11), a thrust bearing shell, a reversing sleeve ring (141), a reversing thrust block (151), a forward thrust block (152) and a forward sleeve ring (142) which are arranged in the thrust bearing shell; it is characterized in that the preparation method is characterized in that,
the damping thrust bearing further comprises a damping element (20), an integrated valve block (30) and a control box (40); the damping elements (20) are uniformly arranged in the forward turning sleeve ring (142) along the circumferential direction, and each damping element (20) comprises a hydraulic cylinder, a damping spring (25), a piston (26), a thrust supporting block (21), a spring pressing cap (23), a magnetic ring (211) and a displacement sensor (29); the rear end of the spring pressing cap (23) is positioned in the hydraulic cylinder, the front end of the spring pressing cap extends out of the middle of the front end of the hydraulic cylinder, the spring pressing cap (23) can move axially relative to the hydraulic cylinder, the thrust supporting block (21) is fixedly arranged at the front end of the spring pressing cap (23), and the thrust supporting block (21) is in contact with the forward thrust block (152); the magnetic ring (211) is fixedly arranged at the rear end of the spring pressing cap (23); the piston (26) is arranged in the cylinder body (24), the damping spring (25) is arranged between the spring pressing cap (23) and the piston (26), and a sealing cavity is formed between the piston (26) and the rear end of the hydraulic cylinder; the displacement sensor (29) is fixedly arranged at the rear end of the hydraulic cylinder;
the vibration reduction elements (20) are mutually connected in parallel, oil inlets of sealing cavities of the vibration reduction elements (20) are connected with the integrated valve block (30) after being connected through oil pipes, and oil inlets and oil return ports of the integrated valve block (30) are connected with a hydraulic system; the displacement sensors (29) of the damping elements (20) are respectively connected with the control box (40), the integrated valve block (30) is connected with the control box (40), and the control box (40) controls the integrated valve block (30) to act according to displacement signals of the displacement sensors (29) to actuate hydraulic pressure, so that the displacement of the propulsion shafting is kept within a design range.
2. The damped thrust bearing based on hydraulic servo control of claim 1 wherein the hydraulic cylinder includes a cylinder block (24), a front end cap (22) and a rear end cap (28), the front end cap (22) and the rear end cap (28) being fixedly mounted at both ends of the cylinder block (24).
3. The damped thrust bearing based on hydraulic servo control of claim 2 wherein the damping element (20) further comprises a transition joint (213) fixedly attached to a rear end of the rear end cover (28), the transition joint (213) axially extending out of the thrust bearing housing for connection to the integration valve block (30).
4. The damped thrust bearing based on hydraulic servo control of claim 2, wherein the displacement sensor (29) is a magnetostrictive displacement sensor, the displacement sensor (29) is fixedly arranged on the rear end cover (28), and the body of the displacement sensor extends into the cylinder body (24); the damping element (20) further comprises a sealing sleeve (27), and the sealing sleeve (27) is sleeved outside the sensor body and fixedly connected with the rear end cover (28).
5. The damped thrust bearing based on hydraulic servo control of claim 2, wherein the outer diameter of the thrust support block (21) is larger than the inner diameter of the front end cover (22), and a protective gap is arranged between the thrust support block (21) and the front end cover (22) to ensure that the displacement of the thrust shaft system does not exceed a limited displacement.
6. The damped thrust bearing based on hydraulic servo control of claim 2 wherein the spring cap (23) is designed with clearance through the front cover (22) to prevent the spring cap (23) from rigidly contacting the front cover (22).
7. The damped thrust bearing based on hydraulic servo control as set forth in claim 1, wherein the magnetic ring (211) is fixedly installed at the rear end of the spring cap (23) by a magnetic ring fixing device, the magnetic ring fixing device comprises a magnetic ring fixing rod (210) and a magnetic ring pressing plate (212), the magnetic ring fixing rod (210) is fixedly installed at the rear end of the spring cap (23), the magnetic ring pressing plate (212) is fixedly installed at the rear end of the magnetic ring fixing rod (210), and the magnetic ring (211) is embedded between the magnetic ring fixing rod (210) and the magnetic ring pressing plate (212).
8. The hydraulic servo control-based damped thrust bearing of claim 1, further comprising a reverse adjustment plate (131) and a forward adjustment plate (132), the reverse adjustment plate (131) disposed between the thrust bearing housing and a reverse collar (141), the forward adjustment plate (132) disposed between the thrust bearing housing and a forward collar (142).
9. The damped thrust bearing according to claim 1 wherein the damped thrust bearing further comprises an upper bearing shell (161) and a lower bearing shell (162), the upper bearing shell (161) and the lower bearing shell (162) being disposed inside the positive bearing ring (142) to provide radial support for the thrust shaft (11).
10. The damped thrust bearing according to claim 1 wherein the control box (40) includes two modes of operation, display and control, wherein the hydraulic servo control system of the thrust bearing is not engaged when the control box (40) is in the display mode; when the control box (40) is in a 'control' mode, a hydraulic servo control system of the thrust bearing participates in work, and at the moment, the control box (40) controls the integrated valve block (30) to act according to a displacement signal of the displacement sensor (29) to actuate hydraulic pressure, so that the displacement of the propulsion shafting is ensured to be kept within a design range.
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| CN202110850204.4A CN113653764A (en) | 2021-07-27 | 2021-07-27 | Damping thrust bearing based on hydraulic servo control |
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| CN202110850204.4A CN113653764A (en) | 2021-07-27 | 2021-07-27 | Damping thrust bearing based on hydraulic servo control |
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| CN113653764A true CN113653764A (en) | 2021-11-16 |
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| CN202110850204.4A Pending CN113653764A (en) | 2021-07-27 | 2021-07-27 | Damping thrust bearing based on hydraulic servo control |
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