CN214161414U - Differential control device for differential feeding in processing of inner hole of propeller - Google Patents
Differential control device for differential feeding in processing of inner hole of propeller Download PDFInfo
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- CN214161414U CN214161414U CN202022745672.9U CN202022745672U CN214161414U CN 214161414 U CN214161414 U CN 214161414U CN 202022745672 U CN202022745672 U CN 202022745672U CN 214161414 U CN214161414 U CN 214161414U
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Abstract
The utility model relates to a large-scale screw machine tool equipment specifically is the differential controlling means that last screw hole processing differential fed. The utility model comprises a main shaft, a feeding mandrel, a differential mechanism and a differential servo motor; the differential mechanism comprises a left half shaft, a right half shaft and a planet carrier; the main shaft and the feeding mandrel are respectively in transmission connection with the planet carrier and the right half shaft through an intermediate transmission mechanism; the differential servo motor is in transmission connection with the left half shaft through a transmission mechanism; by using differential characteristics of differentials, N1+N2=2N0By controlling the rotation speed of the differential servo motorAnd the rotating speed difference between the mandrel and the main shaft is changed to drive the differential feeding mechanism to complete the feeding of the cutter.
Description
Technical Field
The utility model relates to a machining field, especially a differential controlling means that screw hole processing differential feed.
Background
With the development of the ship industry in China towards deep sea and ocean, the demand for large ships is increased, and the demand for matched ultra-large propellers is also generated. With the development of national science and technology and the improvement of comprehensive national force, large and ultra-large propellers are shaped and required to be produced in batches, and processing equipment with stable and efficient processing precision is objectively needed. At present, in the processing production of large propellers, the inner hole and the end face are processed by adopting a numerical control vertical lathe. Due to the special structure of the propeller, the weight of the propeller reaches about 130 tons, the propeller is 2m to 3m high, the diameter of the propeller reaches more than 10m, but the minimum diameter of a machined inner hole is only 0.5m, and the traditional numerical control vertical lathe cannot meet the requirement.
The special machine tool for processing the inner hole of the large-scale propeller generally comprises a rotary boring cutter rest part for boring the inner hole and a feeding part for the boring cutter rest, wherein the axis of a workpiece of the large-scale propeller is vertically fixed on a supporting frame of the special machine tool, and the boring cutter rest part and the feeding part for the boring cutter rest extend upwards into the inner hole from the bottom end of the workpiece of the propeller through a supporting and transmission structure for boring. This support and transmission structure must support the weight of the boring holder portion and the feed portion of the boring holder and withstand the cutting forces of boring; meanwhile, the transmission of the rotary power of the boring cutter rest and the transmission and control of the feeding power are realized. Because the inner hole of the propeller is several meters high and the diameter is only 0.5 meter at least, under the condition of the space, the development of the processing equipment which can bear the weight and the cutting force of a processing tool component at the same time and can transmit the rotary cutting power and control the feeding is difficult, and particularly, the rotary cutting power and the control of the feeding of the tool are transmitted at the same time in a narrow space. The existing design scheme adopts a hollow main shaft and a feeding mandrel arranged in the main shaft, a differential feeding mechanism is arranged at a tool rest end, and the feeding mechanism is driven to feed axially according to the rotating speed difference between the main shaft and the mandrel. However, how to control the difference in the rotation speed between the main shaft and the internally-arranged feeding spindle and finally solve the problem of axial feeding of the tool is not solved.
Disclosure of Invention
The utility model discloses problem that (one) the utility model is to solve: the control of the rotating speed difference between the main shaft and the built-in feeding spindle is realized by controlling the servo motor.
Disclosure of the invention
To above problem, the utility model provides a differential controlling means that screw hole processing differential feed, include:
the main shaft mechanism, the servo driving mechanism, the differential mechanism, the middle transmission mechanism and the differential feeding mechanism are arranged on the special machine tool main body;
the main shaft mechanism comprises a large gear ring, a main shaft, a driving large bevel gear, a feeding mandrel and a driven small bevel gear which are coaxially and vertically arranged; the large gear ring is fixedly connected with the hollow main shaft; the upper end of the main shaft is connected with a differential feed mechanism, and the lower end of the main shaft is fixedly connected with a driving large bevel gear; the feeding mandrel is positioned in the main shaft, the upper end of the feeding mandrel is connected with the differential feeding mechanism, and the lower end of the feeding mandrel is fixedly connected with the driven bevel pinion;
the differential mechanism comprises a differential box and a differential, and the differential comprises a left half shaft, a right half shaft, a planet carrier and a planet carrier gear; the left half shaft and the right half shaft are respectively connected with a planet carrier through bearings, and the planet carrier is connected with the differential case through the bearings; the planet carrier is fixedly connected with the planet carrier gear; the rotating speeds of the left half shaft, the right half shaft and the planet carrier satisfy the following relations:
in the formula, N1Is the rotational speed of the left half shaft; n is a radical of2Is the rotational speed of the right half-shaft; n is a radical of0Is the rotational speed of the planet carrier;
the intermediate transmission mechanism comprises a main shaft transmission mechanism and a feeding spindle transmission mechanism;
the main shaft transmission mechanism comprises a driven large bevel gear, a transmission sleeve, a gear A, a gear B and a gear C; the driving large bevel gear is meshed with the driven large bevel gear, the driven large bevel gear is fixedly connected with a gear A through a transmission sleeve, the gear A is meshed with a gear C, the gear C is fixedly connected with a gear B through a shaft, and the gear B is meshed with a planet carrier gear; the transmission ratio from the driving large bevel gear to the planet carrier gear is 1: 2;
the feeding spindle transmission mechanism comprises a driving bevel pinion, a spline housing and a transmission shaft; the right half shaft is inserted into one end of the transmission shaft through the spline sleeve, the other end of the transmission shaft is fixedly connected with the driving small bevel gear, and the driving small bevel gear is meshed with the driven small bevel gear; the transmission ratio from the right half shaft to the driven bevel pinion is 1: 1;
the servo driving mechanism comprises a differential servo motor, a servo gear shaft and a servo gear; the differential servo motor is fixed on the differential box, and an output shaft of the differential servo motor is fixedly connected with the servo gear shaft; the servo gear shaft is meshed with the servo gear, and the servo gear is fixedly connected with the left half shaft.
Preferably, the differential control device for differential feeding in the processing of the inner hole of the propeller is characterized in that the driving small bevel gear, the driven large bevel gear, the transmission sleeve, the transmission shaft, the spline sleeve and the gear A are coaxially mounted.
The utility model discloses an effect: the utility model combines the two driving rotating speeds of the main shaft driving and the servo driving mechanism driving together through the differential mechanism to form differential speed, thereby realizing the control of the rotating speed of the feeding mandrel; when the main shaft rotates and the differential servo motor does not rotate, the feeding mandrel and the main shaft keep rotating synchronously, and the feeding mechanism does not feed; when the differential servo motor is started, the differential mechanism is used for realizing the differential speed between the mandrel and the main shaft, and driving the differential feeding mechanism to finish the feeding of the cutter.
Drawings
FIG. 1 is a sectional view of the main shaft mechanism and the intermediate transmission mechanism of the present invention;
FIG. 2 is a cross-sectional view of the differential mechanism of the present invention;
fig. 3 is a schematic diagram of the meshing relationship of the differential mechanism of the present invention.
In the figure, 1, a large gear ring; 2. a main shaft; 3-1, driving a large bevel gear; 3-2, driven large bevel gear; 4. a feed spindle; 5-1, driving bevel pinion; 5-2, driven bevel pinion; 6. a transmission sleeve; 7. a drive shaft; 8. a spline housing; 9. a gear A; 10. a differential case; 11. a planet carrier; 12-1, a gear shaft a; 12-2, a gear shaft c; 13. a right half shaft; 14. a left half shaft; 15-1, a gear shaft b; 15-2, a gear shaft d; 16. a differential servo motor; 17. a servo gear shaft; 18. a servo gear; 19. a planet carrier gear; 20. a gear B; 21. gear C; 30. a special machine tool main body.
Detailed Description
The structure and operation of the differential control device for processing differential feed of inner hole of propeller provided by the present invention will now be described in detail with reference to fig. 1, 2 and 3.
Vertical definition: is vertical to the horizontal plane.
Definition of gear shaft: the gear shaft is a structure that the gear and the shaft are integrated, and one end or two ends of the gear are provided with the shaft. When one end is provided with the shaft, the end provided with the shaft is called a shaft end; the other end is a gear end.
The utility model provides a differential controlling means's that screw hole processing differential feed main structure is shown in figure 1, include:
a main shaft mechanism, a servo driving mechanism, a differential mechanism, an intermediate transmission mechanism and a differential feeding mechanism which are arranged on the special machine tool main body 30;
the main shaft mechanism comprises a large gear ring 1, a main shaft 2, a driving large bevel gear 3-1, a feeding spindle 4 and a driven small bevel gear 5-2 which are coaxially and vertically arranged; the large gear ring 1 is fixedly connected with a hollow main shaft 2; the upper end of the main shaft 2 is connected with a differential feed mechanism, and the lower end is fixedly connected with a driving large bevel gear 3-1; the feeding spindle 4 is positioned in the main shaft 2, the upper end of the feeding spindle is connected with the differential feeding mechanism, and the lower end of the feeding spindle is fixedly connected with the driven bevel pinion 5-2.
The main power of the special machine tool drives the main shaft 2 to rotate through the large gear ring 1; the spindle 2 and the feed spindle 4 are connected to a differential feed mechanism that drives the feed of the tool according to the difference in the rotational speed between the spindle 2 and the feed spindle 4. When the main shaft 2 and the feeding mandrel 4 are synchronous, the cutter does not feed; when the rotating speed of the feeding mandrel 4 is greater than that of the main shaft 2, the cutter is fed upwards; otherwise, the feeding is reversely carried out.
The differential mechanism includes a differential case 10 and a differential; the differential is a cylindrical gear differential and comprises a left half shaft 14, a right half shaft 13, a planet carrier 11 and a planet carrier gear; the left half shaft 14 and the right half shaft 13 are respectively connected with the planet carrier 11 through bearings, and the planet carrier 11 is connected with the differential case 10 through a bearing; the planet carrier 11 is fixedly connected with a planet carrier gear 19; the rotating speeds of the left half shaft 14, the right half shaft 13 and the planet carrier 11 satisfy the relationship of the following formula one:
in the formula: n is a radical of1Is the rotational speed of the left half shaft 14; n is a radical of2Is the rotational speed of the right half-shaft 13; n is a radical of0Is the rotational speed of the carrier 11.
According to this formula, N1=2N0-N2(ii) a That is, the rotational speed of the left half-shaft 14 is equal to the difference between the rotational speed of the right half-shaft 13 and twice the rotational speed of the planet carrier 11. Controlling the rotational speed of the left axle shaft 14 controls the difference in rotational speed between the right axle shaft 13 and the planet carrier 11. If the right half-shaft 13 is connected to the feed spindle 4 via an intermediate transmission mechanism and the planet carrier 11 is connected to the main shaft 2 after being decelerated 1/2, it is achieved that the difference in rotational speed between the main shaft 2 and the built-in feed spindle 4 is controlled by controlling the rotational speed of the left half-shaft 14.
According to this concept, the intermediate transmission is designed. The middle transmission mechanism comprises a main shaft transmission mechanism and a feeding mandrel transmission mechanism:
the first part is that the main shaft transmission mechanism comprises a driven large bevel gear 3-2, a transmission sleeve 6, a gear A9, a gear B20 and a gear C21; the driving large bevel gear 3-1 is meshed with the driven large bevel gear 3-2, the driven large bevel gear 3-2 is fixedly connected with a gear A9 through a transmission sleeve 6, the gear A9 is meshed with a gear C21, the gear C21 is fixedly connected with a gear B20 through a shaft, and the gear B20 is meshed with a planet carrier gear 19; the transmission ratio of the driving large bevel gear 3-1 to the planet carrier gear 19 is 1: 2; the cumulative speed ratio from the driving large bevel gear 3-1 to the planet carrier gear 19 is 1:2, i.e. the speed ratio from the main shaft 2 to the planet carrier 11 is 1: 2; the main shaft 2 rotates for one circle, and the planet carrier 11 rotates for half a circle.
The driving small bevel gear 5-1, the driven large bevel gear 3-2, the transmission sleeve 6, the transmission shaft 7, the spline sleeve 8 and the gear A9 are coaxially arranged. Thus, the whole structure of the device is more compact.
The second part, the said feed mandrel drive mechanism includes the small bevel gear 5-1 of initiative, spline housing 8 and drive shaft 7; a right half shaft 13 in the differential is inserted into one end of a transmission shaft 7 through a spline sleeve 8, the other end of the transmission shaft 7 is fixedly connected with a driving small bevel gear 5-1, and the driving small bevel gear 5-1 is meshed with a driven small bevel gear 5-2; the transmission ratio of the right half shaft 13 to the driven bevel pinion 5-2 is 1: 1; since the feed spindle 4 is fixedly connected to the driven bevel pinion 5-2, the transmission ratio of the right half shaft 13 to the feed spindle 4 is also 1: 1.
After the transmission connection between the differential and the main shaft mechanism is realized, the rotation speed of the left half shaft 14 needs to be controlled, so that the rotation speed difference between the main shaft 2 and the feeding spindle 4 can be controlled. For this purpose, a servo driving mechanism is provided, and comprises a differential servo motor 16, a servo gear shaft 17 and a servo gear 18; the differential servo motor 16 is fixed on the differential box 10, and the output shaft of the differential servo motor is fixedly connected with a servo gear shaft 17; the servo gear shaft 17 is engaged with a servo gear 18, and the servo gear 18 is fixedly connected with the left half shaft 14. The left half shaft 14 is driven by the servo driving mechanism.
In this way, the purpose of controlling the rotational speed difference between the main shaft 2 and the feed spindle 4 by controlling the rotational speed of the differential servo motor 16 is achieved.
In the embodiment shown in fig. 2 and 3, the differential is constructed such that the two ends of the planet carrier 11 are two circular end plates with necks and central holes, the central holes are provided with bearings, the two end plates are coaxially and fixedly connected into a whole through an intermediate support structure, and one of the end plates is fixedly connected with the planet carrier gear 19;
the left half shaft 14 and the right half shaft 13 are gear shafts respectively, and are provided with gear ends and shaft ends respectively, the end faces of the two gear ends are opposite and coaxially arranged in the planet carrier 11, and the two shaft ends are connected to the planet carrier 11 through bearings arranged in the central hole respectively;
the planet carrier 11 is internally provided with four planet gears which are a gear shaft a12-1, a gear shaft b15-1, a gear shaft c12-2 and a gear shaft d 15-2; the two ends of the gear shaft a12-1, the gear shaft b15-1, the gear shaft c12-2 and the gear shaft d15-2 are respectively connected to the end plates of the planet carrier 11 through bearings; the left half shaft 14 is meshed with a gear shaft a12-1, the gear shaft a12-1 is meshed with a gear shaft d15-2, and the gear shaft d15-2 is meshed with the right half shaft 13; forming a linkage between the left and right half- shafts 14, 13. Symmetrically, the other set of planet gears forms the other set of linkages, with left axle shaft 14 meshing with gear shaft c12-2, gear shaft c12-2 meshing with gear shaft b15-1, and gear shaft b15-1 meshing with right axle shaft 13.
The four planetary gears rotate together with the planet carrier, are meshed with each other in pairs and are meshed with the left half shaft 14 and the right half shaft 13 respectively, so that the differential relation among the left half shaft 14, the right half shaft 13 and the planet carrier 11 is formed:
in the formula: n is a radical of1Is the rotational speed of the left half shaft 14; n is a radical of2Is the rotational speed of the right half-shaft 13; n is a radical of0Is the rotational speed of the carrier 11.
The working process of the solution proposed by the present invention is described below with reference to fig. 1, fig. 2 and fig. 3:
in the first case, the main shaft 2 rotates, the differential servo motor 16 does not rotate:
starting a spindle motor, driving a large gear ring 1 to rotate through multi-stage gear transmission in a spindle box, driving a spindle 2 to rotate through a flat key by the large gear ring 1, driving a pair of driving large bevel gears 3-1 to rotate by the spindle 2, driving a transmission sleeve 6 to rotate through driven large bevel gears 3-2 by the driving large bevel gears 3-1, driving a gear A9 inside a differential mechanism to rotate through the flat key by the transmission sleeve 6, driving a gear A9 to rotate by the gear A9, and driving a coaxial gear B20 to drive a planet carrier gear 19 to rotate; the planet carrier gear 19 drives the planet carrier 11 to rotate through a flat key, and the planet carrier 11 drives four planet gear shafts a12-1, a gear shaft c12-2, a gear shaft b15-1 and a gear shaft d15-2 in the planet carrier to revolve; at the moment, the differential servo motor 16 does not rotate, the left half shaft 14 does not rotate, and the four planetary gears rotate to drive the right half shaft 13 to rotate; the right half shaft 13 drives the transmission shaft 7 to rotate through the spline sleeve 8, and further drives the driving small bevel gear 5-1 and the driven small bevel gear 5-2 meshed with the driving small bevel gear to rotate, and further drives the feeding mandrel 4 to rotate. According to the formula one, at the moment, the rotation speed of the right half shaft 13 is twice that of the planet carrier 11, and since the rotation speed ratio of the main shaft 2 to the planet carrier 11 is 1:2, the rotation speed of the feeding spindle 4 is the same as that of the main shaft 2 at the moment, the direction is the same, no rotation speed difference exists between the feeding spindle 4 and the main shaft 2, and the differential feeding mechanism does not drive the tool to feed.
In the second case, the spindle 2 rotates while the differential servo motor 16 is activated:
the servo motor 16 drives the gear shaft 17 and the gear 18 to rotate, the gear 18 drives the left half shaft 14 to rotate through a flat key, and the left half shaft 14 is meshed with the gear shaft a, the gear shaft c12-2, the gear shaft b15-1 and the gear shaft d 15-2; meanwhile, because the main shaft 2 drives the planet carrier 11 to rotate, the rotating speed of the right half shaft 13 is the difference between twice of the rotating speed of the planet carrier 11 and the rotating speed of the left half shaft 14; when the servo motor 16 drives the left half shaft 14 to rotate in the same direction as the planet carrier 11, the rotating speed of the right half shaft 13 is reduced, and vice versa; the right half shaft 13 drives the transmission shaft 7 to rotate through the spline housing 8, so as to drive the driving small bevel gear 5-1, the driven small bevel gear 5-2 and the feeding spindle 4 to rotate, the rotation speed of the right half shaft 13 relative to the planet carrier 11 changes, so that a rotation speed difference between the feeding spindle 4 and the main shaft 2 is formed, and the differential feeding mechanism drives a cutter to feed according to the size and the direction of the rotation speed difference, so that the feeding function of the cutter is realized.
Claims (2)
1. A differential control device for differential feeding of processing of inner holes of propellers comprises:
a main shaft mechanism, a servo driving mechanism, a differential mechanism, an intermediate transmission mechanism and a differential feeding mechanism which are arranged on a special machine tool main body (30);
the main shaft mechanism comprises a large gear ring (1), a main shaft (2), a driving large bevel gear (3-1), a feeding mandrel (4) and a driven small bevel gear (5-2) which are coaxially and vertically arranged; the large gear ring (1) is fixedly connected with the hollow main shaft (2); the upper end of the main shaft (2) is connected with a differential feed mechanism, and the lower end is fixedly connected with a driving large bevel gear (3-1); the feeding mandrel (4) is positioned in the main shaft (2), the upper end of the feeding mandrel is connected with the differential feeding mechanism, and the lower end of the feeding mandrel is fixedly connected with the driven bevel pinion (5-2);
the differential mechanism comprises a differential box (10) and a differential, wherein the differential comprises a left half shaft (14), a right half shaft (13), a planet carrier (11) and a planet carrier gear (19); the left half shaft (14) and the right half shaft (13) are respectively connected with the planet carrier (11) through bearings, and the planet carrier (11) is connected with the differential case (10) through the bearings; the planet carrier (11) is fixedly connected with the planet carrier gear (19); the rotating speeds of the left half shaft (14), the right half shaft (13) and the planet carrier (11) satisfy the following relations:
in the formula, N1Is the rotational speed of the left half shaft (14); n is a radical of2Is the rotation speed of the right half shaft (13); n is a radical of0Is the rotational speed of the planet carrier (11);
the intermediate transmission mechanism comprises a main shaft transmission mechanism and a feeding spindle transmission mechanism;
the main shaft transmission mechanism comprises a driven large bevel gear (3-2), a transmission sleeve (6), a gear A (9), a gear B (20) and a gear C (21); the driving large bevel gear (3-1) is meshed with the driven large bevel gear (3-2), the driven large bevel gear (3-2) is fixedly connected with a gear A (9) through a transmission sleeve (6), the gear A (9) is meshed with a gear C (21), the gear C (21) is fixedly connected with a gear B (20) through a shaft, and the gear B (20) is meshed with a planet carrier gear (19); the transmission ratio of the driving large bevel gear (3-1) to the planet carrier gear (19) is 1: 2;
the feeding spindle transmission mechanism comprises a driving bevel pinion (5-1), a spline sleeve (8) and a transmission shaft (7); the right half shaft (13) is inserted into one end of the transmission shaft (7) through the spline sleeve (8), the other end of the transmission shaft (7) is fixedly connected with the driving small bevel gear (5-1), and the driving small bevel gear (5-1) is meshed with the driven small bevel gear (5-2); the transmission ratio from the right half shaft (13) to the driven bevel pinion (5-2) is 1: 1;
the servo driving mechanism comprises a differential servo motor (16), a servo gear shaft (17) and a servo gear (18); the differential servo motor (16) is fixed on the differential box (10), and the output shaft of the differential servo motor is fixedly connected with a servo gear shaft (17); the servo gear shaft (17) is meshed with a servo gear (18), and the servo gear (18) is fixedly connected with the left half shaft (14).
2. The differential control device for the internal hole machining differential feeding of the propeller according to claim 1 is characterized in that the driving small bevel gear (5-1), the driven large bevel gear (3-2), the transmission sleeve (6), the transmission shaft (7), the spline sleeve (8) and the gear shell (9) are coaxially arranged.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022745672.9U CN214161414U (en) | 2020-11-24 | 2020-11-24 | Differential control device for differential feeding in processing of inner hole of propeller |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202022745672.9U CN214161414U (en) | 2020-11-24 | 2020-11-24 | Differential control device for differential feeding in processing of inner hole of propeller |
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| Publication Number | Publication Date |
|---|---|
| CN214161414U true CN214161414U (en) | 2021-09-10 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202022745672.9U Active CN214161414U (en) | 2020-11-24 | 2020-11-24 | Differential control device for differential feeding in processing of inner hole of propeller |
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| Country | Link |
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| CN (1) | CN214161414U (en) |
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