CN112125189A - Normally closed braking double-speed planetary transmission structure - Google Patents
Normally closed braking double-speed planetary transmission structure Download PDFInfo
- Publication number
- CN112125189A CN112125189A CN202011141785.6A CN202011141785A CN112125189A CN 112125189 A CN112125189 A CN 112125189A CN 202011141785 A CN202011141785 A CN 202011141785A CN 112125189 A CN112125189 A CN 112125189A
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- piston
- gear ring
- spring
- inner gear
- sun gear
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/02—Driving gear
- B66D1/14—Power transmissions between power sources and drums or barrels
- B66D1/22—Planetary or differential gearings, i.e. with planet gears having movable axes of rotation
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
- B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
- B66D1/28—Other constructional details
Abstract
The invention relates to a normally closed braking double-speed planetary transmission structure, and belongs to the field of transmission structures. The solar water heater comprises a cylinder body, a primary sun gear, a secondary sun gear and an inner gear ring, wherein the primary sun gear, the secondary sun gear and the inner gear ring are rotatably arranged in the cylinder body; the second-stage sun gear is fixedly provided with a planet carrier, and the planet carrier rotates around the axis of the second-stage sun gear along with the second-stage sun gear; the planet carrier is rotatably provided with a planet wheel, the rotation axis of the planet wheel is parallel to the rotation axis of the secondary sun wheel, the planet wheel is respectively meshed with the primary sun wheel and the inner gear ring, and the planet wheel rotates around the axis of the secondary sun wheel along with the planet carrier; normally closed brakes are arranged between the inner gear ring and the first-stage sun gear and between the inner gear ring and the cylinder body. The invention has the function of normally closed braking. The transmission path is changed by opening and closing the normally closed brake, and the use requirements of light load high speed and heavy load low speed are met.
Description
Technical Field
The invention belongs to the field of marine winch transmission structures, and relates to a normally closed brake double-speed planetary transmission structure.
Background
In the field of marine winches, a common winch planetary reducer with a normally closed braking device only has one gear rotating speed, and can only meet the actual use of light-load high-speed and heavy-load low-speed working conditions through motor frequency conversion. The common planet structure is a single-speed reducer structure with a normally-closed braking device, cannot meet the requirements of double-working-condition movement of light load, high speed, heavy load and low speed, and needs to change the output rotating speed through motor frequency conversion. This results in the motor being generally selected to be large and not delivering full power. In order to exert the full power of the motor, reduce the motor model and the complexity of the electric appliance and meet the use requirements of other power sources, a double-speed planetary transmission structure with a normally closed braking function is required to meet the use requirements of light load high speed and heavy load low speed.
Disclosure of Invention
In view of the above, the present invention provides a normally closed braking two-speed planetary transmission structure, which can perform normally closed braking and simultaneously satisfy the use requirements of light load high speed and heavy load low speed.
In order to achieve the purpose, the invention provides the following technical scheme: a normally-closed braking double-speed planetary transmission structure comprises a cylinder body, a primary sun gear, a secondary sun gear and an inner gear ring, wherein the primary sun gear, the secondary sun gear and the inner gear ring are rotatably arranged in the cylinder body and are coaxially arranged; the secondary sun gear is fixedly provided with a planet carrier, and the planet carrier rotates around the axis of the secondary sun gear along with the secondary sun gear; the planet carrier is rotatably provided with a planet wheel, the rotation axis of the planet wheel is parallel to the rotation axis of the secondary sun wheel, the planet wheel is respectively meshed with the primary sun wheel and the inner gear ring, and the planet wheel rotates around the axis of the secondary sun wheel along with the planet carrier; and normally-closed brakes are arranged between the inner gear ring and the primary sun gear and between the inner gear ring and the cylinder body.
Optionally, a normally closed brake between the ring gear and the primary sun gear is a first brake, the first brake includes a first piston, a first spring, and a first friction plate set, and the first spring, the first piston, and the first friction plate set are sequentially arranged along the axis direction of the ring gear; the first spring is fixedly arranged at one end far away from the first piston, the other end of the first spring acts on the first piston, the first spring and the first piston are arranged along the axis direction of the inner gear ring, the first piston slides in the cylinder body in a reciprocating mode along the axis direction of the inner gear ring, a first friction plate gasket is arranged on the inner gear ring, the first friction plate set comprises a plurality of friction plates which are respectively arranged on the inner gear ring and the first-stage sun gear, the first spring tightly presses the friction plates on the first friction plate gasket through the first piston, a hydraulic cavity is arranged between the piston and the cylinder body, and the hydraulic cavity drives the first spring to compress the first spring.
Optionally, a bearing seat is arranged between the first piston and the first friction plate set, the first spring presses the first friction plate sets on the first friction plate washer through the first piston and the bearing seat, a rotating bearing is arranged between the first piston and the bearing seat, and the bearing seat is connected to the first piston in a manner of rotating around the axis direction of the inner gear ring through the rotating bearing.
Optionally, an input shaft is further disposed in the cylinder body, the input shaft and the primary sun gear are coaxially disposed, the primary sun gear is fixedly connected to the input shaft, and the first friction plate group is disposed between the inner gear ring and the input shaft.
Optionally, the friction plates on the inner gear ring and the friction plates on the first-stage sun gear are sequentially arranged in a staggered manner.
Optionally, a normally closed brake between the cylinder and the ring gear is a second brake, the second brake includes a second piston, a second spring, and a second friction plate set, and the second spring, the second piston, and the second friction plate set are sequentially arranged along the axis direction of the ring gear; the second spring and the second piston are arranged along the axial direction of the inner gear ring, one end, far away from the second piston, of the second spring is fixedly arranged, the other end of the second spring acts on the second piston, and the second piston slides in the cylinder body in a reciprocating manner along the axial direction of the inner gear ring; be provided with the second friction disc packing ring on the cylinder body, second friction disc group includes a plurality of friction discs, and is a plurality of the friction disc sets up respectively the cylinder body reaches on the inner ring gear, the second spring passes through the second piston will the friction disc compresses tightly on the second friction disc packing ring, the second piston with be provided with the second hydraulic chamber between the cylinder body, the drive of second hydraulic chamber the second spring compression the second spring.
Optionally, the friction plates on the inner gear ring and the friction plates on the cylinder body are sequentially arranged in a staggered manner.
Optionally, a planet pin is arranged on the planet carrier, and the planet wheel is rotatably connected to the planet carrier through the planet pin.
The invention has the beneficial effects that: (1) and normally closed brakes are arranged between the inner gear ring and the primary sun gear and between the inner gear ring and the cylinder body, and have a normally closed braking function. (2) The transmission path is changed by opening and closing the normally closed brake, and the use requirements of light load high speed and heavy load low speed are met.
Additional advantages, objects, and features of the invention will be set forth in part in the description which follows and in part will become apparent to those having ordinary skill in the art upon examination of the following or may be learned from practice of the invention. The objectives and other advantages of the invention may be realized and attained by the means of the instrumentalities and combinations particularly pointed out hereinafter.
Drawings
For the purposes of promoting a better understanding of the objects, aspects and advantages of the invention, reference will now be made to the following detailed description taken in conjunction with the accompanying drawings in which:
FIG. 1 is a schematic structural diagram of a normally closed braking two-speed planetary transmission structure;
fig. 2 is a partial enlarged view of a normally closed brake two-speed planetary transmission configuration.
Reference numerals: a primary sun wheel 1, an input shaft 2, a skeleton oil seal 3, a rotary bearing 4, a bearing seat 5, a source power mounting seat 6, a first piston 7, an auxiliary cylinder 8, a second piston 9, a main cylinder 10, an inner gear ring 11, a spline seat 12, a second friction plate gasket 13, a roller pin 14, a planet wheel 15, an O-shaped sealing ring 16, a planet carrier 17, a secondary planet carrier 18, a planet carrier pin shaft 19 and a planet wheel gasket 20, the shaft snap spring 21, the second-stage sun gear 22, the third shaft snap spring 23, the hole snap spring 24, the second rotating bearing 25, the hole retainer ring 26, the first friction plate washer 27, the second friction plate set 28, the first friction plate set 29, the second piston seal 30, the second spring 31, the screw 32, the third rotating bearing 33, the first piston seal 34, the second O-shaped seal ring 35, the second screw 36, the first spring 37, the second shaft snap spring 38 and the first high-pressure port 39.
Detailed Description
The embodiments of the present invention are described below with reference to specific embodiments, and other advantages and effects of the present invention will be easily understood by those skilled in the art from the disclosure of the present specification. The invention is capable of other and different embodiments and of being practiced or of being carried out in various ways, and its several details are capable of modification in various respects, all without departing from the spirit and scope of the present invention. It should be noted that the drawings provided in the following embodiments are only for illustrating the basic idea of the present invention in a schematic way, and the features in the following embodiments and examples may be combined with each other without conflict.
Wherein the showings are for the purpose of illustrating the invention only and not for the purpose of limiting the same, and in which there is shown by way of illustration only and not in the drawings in which there is no intention to limit the invention thereto; to better illustrate the embodiments of the present invention, some parts of the drawings may be omitted, enlarged or reduced, and do not represent the size of an actual product; it will be understood by those skilled in the art that certain well-known structures in the drawings and descriptions thereof may be omitted.
The same or similar reference numerals in the drawings of the embodiments of the present invention correspond to the same or similar components; in the description of the present invention, it should be understood that if there is an orientation or positional relationship indicated by terms such as "upper", "lower", "left", "right", "front", "rear", etc., based on the orientation or positional relationship shown in the drawings, it is only for convenience of description and simplification of description, but it is not an indication or suggestion that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and therefore, the terms describing the positional relationship in the drawings are only used for illustrative purposes, and are not to be construed as limiting the present invention, and the specific meaning of the terms may be understood by those skilled in the art according to specific situations.
Referring to fig. 1 to 2, the normally closed braking double-speed planetary transmission structure includes a cylinder, and a primary sun gear 1, a secondary sun gear 22, and an inner gear ring 11 rotatably disposed in the cylinder, wherein the primary sun gear 1, the secondary sun gear 22, and the inner gear ring 11 are coaxially disposed. The second-stage sun gear 22 is fixedly provided with a planet carrier 17, and the planet carrier 17 rotates around the axis of the second-stage sun gear 22 along with the second-stage sun gear 22. The planet carrier 17 is provided with planet wheels 15 in a rotating mode, the rotating axis of the planet wheels 15 is parallel to the rotating axis of the secondary sun wheel 22, the planet wheels 15 are respectively meshed with the primary sun wheel 1 and the inner gear ring 11, and the planet wheels 15 rotate around the axis of the secondary sun wheel 22 along with the planet carrier 17. Normally closed brakes are arranged between the inner gear ring 11 and the first-stage sun gear 1 and between the inner gear ring 11 and the cylinder body. An input shaft 2 is further arranged in the cylinder body, the input shaft 2 and the primary sun gear 1 are coaxially arranged, the primary sun gear 1 is fixedly connected to the input shaft 2, and the first friction plate group 29 is arranged between the internal gear ring 11 and the input shaft 2. The planet carrier 17 is provided with a planet pin shaft, and the planet wheel 15 is rotationally connected to the planet carrier 17 through the planet pin shaft.
The normally closed brake between the ring gear 11 and the primary sun gear 1 is a first brake, the first brake comprises a first piston 7, a first spring 37 and a first friction plate group 29, and the first spring 37, the first piston 7 and the first friction plate group 29 are sequentially arranged along the axis direction of the ring gear 11. One end of the first spring 37, which is far away from the first piston 7, is fixedly arranged, the other end of the first spring 37 acts on the first piston 7, the first spring 37 and the first piston 7 are arranged along the axis direction of the inner gear ring 11, the first piston 7 slides in a reciprocating manner in the cylinder body along the axis direction of the inner gear ring 11, the inner gear ring 11 is provided with a first friction plate washer 27, the first friction plate group 29 comprises a plurality of friction plates, the friction plates are respectively arranged on the inner gear ring 11 and the first-stage sun gear 1, and the friction plates on the inner gear ring 11 and the friction plates on the first-stage sun gear 1 are sequentially arranged in a staggered.
The first spring 37 presses the friction plates against the first friction plate washer 27 through the first piston 7, and a hydraulic chamber is provided between the piston and the cylinder, and drives the first spring 37 to compress the first spring 37. A bearing seat 5 is arranged between the first piston 7 and the first friction plate set 29, the first spring 37 presses the first friction plate sets 29 on the first friction plate washer 27 through the first piston 7 and the bearing seat 5, a rotating bearing 4 is arranged between the first piston 7 and the bearing seat 5, and the bearing seat 5 is connected to the first piston 7 in a manner of rotating around the axis direction of the inner gear ring 11 through the rotating bearing 4.
The normally closed brake between the cylinder body and the ring gear 11 is a second brake, the second brake comprises a second piston 9, a second spring 31 and a second friction plate group 28, and the second spring 31, the second piston 9 and the second friction plate group 28 are sequentially arranged along the axis direction of the ring gear 11. The second spring 31 and the second piston 9 are arranged along the axial direction of the ring gear 11, one end of the second spring 31 far away from the second piston 9 is fixedly arranged, the other end of the second spring 31 acts on the second piston 9, and the second piston 9 slides in the cylinder body in a reciprocating manner along the axial direction of the ring gear 11. The cylinder body is provided with a second friction plate washer 13, the second friction plate group 28 comprises a plurality of friction plates which are respectively arranged on the cylinder body and the inner gear ring 11, and the friction plates on the inner gear ring 11 and the friction plates on the cylinder body are sequentially arranged in a staggered manner. The second spring 31 presses the friction plate against the second friction plate washer 13 through the second piston 9, and a second hydraulic chamber is arranged between the second piston 9 and the cylinder and drives the second piston 9 to compress the second spring 31.
In this embodiment, the planetary gear set further includes a spline housing 12, a secondary planet carrier 18, a third shaft snap spring 23, a second rolling bearing 25, a third rolling bearing 33, a first piston seal 34, a second O-ring seal 35, a second screw 36, and a second shaft snap spring 38. The input shaft 2 is connected with the first-stage sun gear 1, the framework oil seal 3, the rotating bearing 4 and the first friction plate group 29, and power is transmitted to the first-stage sun gear 1 through the input shaft 2. The internal spline of the first friction plate set 29 is connected with the external spline of the input shaft 2, so that the input shaft 2 is normally closed and braked, the rotating bearing 4 is used for positioning the input shaft 2, and the framework oil seal 3 is used for sealing the input shaft 2.
The cylinder body comprises a main cylinder body 10 and an auxiliary cylinder body 8, and an active power mounting seat 6 is arranged on the auxiliary cylinder body 8. The source power mounting seat 6, the auxiliary cylinder body 8, the main cylinder body 10 and the spline seat 12 are fixedly connected through a screw 32 and a second screw 36; the source power mounting seat 6 is also connected with the outer rings of the framework oil seal 3 and the rotating bearing 4, and plays a role in fixing the framework oil seal 3 and the rotating bearing 4. The O-ring 16 at the junction is sealed.
A hole retaining ring 26 is provided in the ring gear 11, and the hole retaining ring 26 is used to fix the first friction plate washer 27. The bearing seat 5, the first piston 7, the auxiliary cylinder 8, the inner gear ring 11, the hole retainer ring 26, the first friction plate washer 27, the first friction plate group 29, the rotary bearing 33, the first piston seal 34, the first spring 37 and the second shaft retainer spring 38 form a first brake, and the hole retainer ring 26 axially fixes the first friction plate washer 27 on the inner gear ring 11; the first friction plate group 29 is respectively connected with the input shaft 2 and the inner gear ring 11 through splines and is arranged above the first friction plate washer 27; the framework oil seal 33 is connected with the bearing seat 5 and the first piston 7 through the matching of the inner ring and the outer ring, and is arranged above the first friction plate group 29,
the outer rings of the bearing seat 5 and the framework oil seal 33 can rotate; a first spring 37 is uniformly arranged in the first piston 7, the first spring 37 is used for driving the mounting base 6, a first hydraulic cavity is sealed 34 between the bearing block 5 and the auxiliary cylinder body 8 through the first piston, and the opening and closing of the first brake are realized by adding and breaking the pressure of the hydraulic cavity.
The second shaft snap spring 38 is mounted on the outer circle of the bearing seat 5 for preventing the bearing seat 5 and the first piston 7 from being accidentally disengaged at the third rotary bearing 33, and a small gap is formed between the second shaft snap spring 38 and the plane of the first piston 7 for preventing the first piston 7 from being pressed downwards, so that when the first friction plate set 29 is closed, interference friction is generated when the second shaft snap spring 38 and the first piston 7 move relatively.
The inner gear ring 11 is axially and radially fixed with the spline base 12 through a third shaft snap spring 23, a hole snap spring 24 and a second rotating bearing 25, and the inner gear ring 11 and the second rotating bearing 25 can rotate. The axial fixation makes the first friction plate set 29 axially fixed, and the radial fixation ensures the normal operation of the spline connection and the gear connection.
The upper part of the first spring 37 is fixed on the power source mounting seat 6, and the lower part of the first spring 37 is in contact with the first piston 7 and is in a compressed state. Because the source power mounting seat 6 and the inner gear ring 11 are axially fixed, the expansion force of the first spring 37 compresses the first piston 7, the bearing seat 5 and the first friction plate group 29, and a normally closed braking effect is achieved. High-pressure oil enters through the first high-pressure port 39, the first piston 7 moves upwards under pressure until the first piston contacts the source power mounting seat 6, at the moment, the first friction plate set 29 is released, and the primary sun gear 1 and the input shaft 2 can rotate freely.
A second piston 9, a main cylinder body 10, an inner gear ring 11, a spline seat 12, a second friction plate gasket 13, a second friction plate group 28, a second piston seal 30 and a second spring 31 form a main body of the second brake, and the second friction plate gasket 13 is arranged above the ring surface of the spline seat 12; the second friction plate group 28 is respectively in splined connection with the inner gear ring 11 and the spline seat 12 through an inner spline and an outer spline and is arranged above the second friction plate washer 13; a second spring 31 is uniformly arranged in the second piston 9 and pressed above the second friction plate group 28, a second hydraulic cavity is formed between the second piston and the main cylinder 10 through a second piston seal 30, and the opening and closing of the second brake are realized through adding and breaking pressure.
The upper part of the second spring 31 is connected on the auxiliary cylinder 8, and the lower part is pressed on the second piston 9; because the auxiliary cylinder body 8, the main cylinder body 10 and the spline seat 12 are axially fixed, the second spring 31 expansion force compresses the second friction plate washer 13 and the second friction plate set 28, and a normally-closed braking effect is achieved. High-pressure oil enters the second hydraulic cavity through the second high-pressure port, the second hydraulic cavity moves upwards under pressure until the second hydraulic cavity is in contact with the auxiliary cylinder body 8, at the moment, the second friction plate set 28 is released, and the inner gear ring 11 can rotate freely.
The primary sun gear 1, the inner gear ring 11, the roller pins 14, the planet gears 15, the planet carrier 17, the planet carrier pin shafts 19, the planet gear gaskets 20 and the shaft clamp springs 21 form primary planetary transmission, the planet gears 15 are simultaneously meshed with the primary sun gear 1 and the inner gear ring 11 through tooth parts to realize power transmission, and the insides of the planet gears 15 are connected with the planet carrier 17 through the roller pins 14, the planet carrier pin shafts 19, the planet gear gaskets 20 and the shaft clamp springs 21. The planetary gear 15 can rotate in the circumferential direction under the condition of axial and radial fixation.
Under the condition that the first brake is opened and the second brake is closed, the inner gear ring 11 is circumferentially fixed, power is sequentially transmitted through the input shaft 2, the first-stage sun gear 1, the planet gear 15, the planet carrier pin shaft 19 and the planet carrier 17, and finally is connected with the second-stage sun gear 22 through the planet carrier 17 and transmitted to the next stage, and at the moment, the second-stage sun gear 22 is low in rotating speed and large in torque. Under the conditions that the first brake is closed and the second brake is opened, the inner gear ring 11 can rotate freely in the circumferential direction, the first-stage sun gear 1, the input shaft 2, the inner gear ring 11, the planet gear 15, the planet carrier 17, the planet carrier pin shaft 19 and the first friction plate set 29 are axially fixed, the power of the input shaft 2 is sequentially transmitted through the first friction plate set 29, the inner gear ring 11, the planet gear 15, the planet carrier pin shaft 19, the planet carrier 17, the first-stage sun gear 1, the planet gear 15, the planet carrier pin shaft 19 and the planet carrier 17, and finally is connected with the second-stage sun gear 22 through the planet carrier 17 and transmitted to the next stage, and at the moment, the second. The inner spline of the inner gear ring 11 is connected with the first friction plate set 29, the outer spline is connected with the second friction plate set 28, and the inner gear ring 11 has two working states of rotation and static.
When the first friction plate group 29 operates, the input shaft 2 operates, the inner gear ring 11 is fixed, in order to ensure smooth oil paths inside the first friction plate group 29, several spline teeth of the input shaft 2 are uniformly distributed and removed, and vertical rectangular grooves are uniformly distributed at the root of an inner spline of the inner gear ring 11 along the tooth direction, so that when the first friction plate group 29 operates relatively, lubricating oil forms circulation to take away internal heat in time. When the second friction plate group 28 operates, the inner gear ring 11 operates, in order to ensure that the oil circuit inside the first friction plate group 29 is smooth, small holes are formed at the bottom of the vertical rectangular groove of the inner gear ring 11 and are aligned with the external spline grinding plates, and meanwhile, vertical rectangular grooves are uniformly distributed at the root of the spline seat 12 along the tooth direction. When the inner gear ring 11 runs at a high speed, oil is thrown into the grinding plates through the small holes and returns to the inside of the box body along the rectangular grooves in the spline seat 12 after passing through the grinding plates, and therefore when the friction plates run relatively, lubricating oil can take away internal heat in time.
Finally, the above embodiments are only intended to illustrate the technical solutions of the present invention and not to limit the present invention, and although the present invention has been described in detail with reference to the preferred embodiments, it will be understood by those skilled in the art that modifications or equivalent substitutions may be made on the technical solutions of the present invention without departing from the spirit and scope of the technical solutions, and all of them should be covered by the claims of the present invention.
Claims (8)
1. A normally closed braking double-speed planetary transmission structure is characterized in that: the solar water heater comprises a cylinder body, a primary sun gear, a secondary sun gear and an inner gear ring, wherein the primary sun gear, the secondary sun gear and the inner gear ring are rotatably arranged in the cylinder body and are coaxially arranged;
the secondary sun gear is fixedly provided with a planet carrier, and the planet carrier rotates around the axis of the secondary sun gear along with the secondary sun gear;
the planet carrier is rotatably provided with a planet wheel, the rotation axis of the planet wheel is parallel to the rotation axis of the secondary sun wheel, the planet wheel is respectively meshed with the primary sun wheel and the inner gear ring, and the planet wheel rotates around the axis of the secondary sun wheel along with the planet carrier;
and normally-closed brakes are arranged between the inner gear ring and the primary sun gear and between the inner gear ring and the cylinder body.
2. The normally closed brake two-speed planetary transmission structure as claimed in claim 1, wherein: the normally closed brake between the inner gear ring and the primary sun gear is a first brake, the first brake comprises a first piston, a first spring and a first friction plate set, and the first spring, the first piston and the first friction plate set are sequentially arranged along the axis direction of the inner gear ring;
the first spring is fixedly arranged at one end far away from the first piston, the other end of the first spring acts on the first piston, the first spring is arranged in the axial direction of the inner gear ring, the first piston slides in the cylinder body in a reciprocating mode in the axial direction of the inner gear ring, a first friction plate washer is arranged on the inner gear ring, the first friction plate set comprises a plurality of friction plates which are respectively arranged on the inner gear ring and the first-stage sun gear, the first spring tightly presses the friction plates on the first friction plate washer through the first piston, a hydraulic cavity is arranged between the piston and the cylinder body, and the hydraulic cavity drives the first spring to compress the first spring.
3. The normally closed brake two-speed planetary transmission structure as claimed in claim 2, wherein: a bearing seat is arranged between the first piston and the first friction plate group, the first spring tightly presses the first friction plate group on the first friction plate washer through the first piston and the bearing seat, a rotating bearing is arranged between the first piston and the bearing seat, and the bearing seat is rotatably connected to the first piston through the rotating bearing in the axial direction of the inner gear ring.
4. The normally closed brake two-speed planetary transmission structure as claimed in claim 2, wherein: an input shaft is further arranged in the cylinder body, the input shaft and the primary sun gear are coaxially arranged, the primary sun gear is fixedly connected to the input shaft, and the first friction plate group is arranged between the inner gear ring and the input shaft.
5. The normally closed brake two-speed planetary transmission structure as claimed in claim 2, wherein: the friction plates on the inner gear ring and the friction plates on the first-stage sun gear are sequentially arranged in a staggered mode.
6. The normally closed brake two-speed planetary transmission structure as claimed in claim 1, wherein: the normally closed brake between the cylinder body and the inner gear ring is a second brake, the second brake comprises a second piston, a second spring and a second friction plate group, and the second spring, the second piston and the second friction plate group are sequentially arranged along the axis direction of the inner gear ring;
the second spring and the second piston are arranged along the axial direction of the inner gear ring, one end, far away from the second piston, of the second spring is fixedly arranged, the other end of the second spring acts on the second piston, and the second piston slides in the cylinder body in a reciprocating manner along the axial direction of the inner gear ring;
be provided with the second friction disc packing ring on the cylinder body, second friction disc group includes a plurality of friction discs, and is a plurality of the friction disc sets up respectively the cylinder body reaches on the inner ring gear, the second spring passes through the second piston will the friction disc compresses tightly on the second friction disc packing ring, the second piston with be provided with the second hydraulic chamber between the cylinder body, the drive of second hydraulic chamber the second spring compression the second spring.
7. The normally closed brake two-speed planetary transmission structure as in claim 6, wherein: the friction plates on the inner gear ring and the friction plates on the cylinder body are sequentially arranged in a staggered mode.
8. The normally closed brake two-speed planetary transmission structure as claimed in claim 1, wherein: the planet carrier is provided with a planet pin shaft, and the planet wheel is rotationally connected to the planet carrier through the planet pin shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011141785.6A CN112125189A (en) | 2020-10-22 | 2020-10-22 | Normally closed braking double-speed planetary transmission structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011141785.6A CN112125189A (en) | 2020-10-22 | 2020-10-22 | Normally closed braking double-speed planetary transmission structure |
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| Publication Number | Publication Date |
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| CN112125189A true CN112125189A (en) | 2020-12-25 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011141785.6A Pending CN112125189A (en) | 2020-10-22 | 2020-10-22 | Normally closed braking double-speed planetary transmission structure |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101648683A (en) * | 2009-07-23 | 2010-02-17 | 上海大屯能源股份有限公司 | Endless rope speed regulation mechanical winch driving device used for mine |
| CN101670989A (en) * | 2009-09-25 | 2010-03-17 | 沈荣骥 | Compact-type built-in differential velocity regulating winch |
| CN102320528A (en) * | 2011-06-20 | 2012-01-18 | 康少松 | Hoisting mechanism of double-speed accelerated lowering device for crane |
| CN103883686A (en) * | 2014-03-11 | 2014-06-25 | 徐州科源液压股份有限公司 | Double-speed ratio walking speed reducer |
| CN205244272U (en) * | 2015-12-31 | 2016-05-18 | 杨崇庆 | Utilize double -brake to realize that planetary reducer of double speed work constructs |
| CN211371178U (en) * | 2019-12-10 | 2020-08-28 | 南京高精齿轮集团有限公司 | Double-speed-ratio gearbox |
-
2020
- 2020-10-22 CN CN202011141785.6A patent/CN112125189A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101648683A (en) * | 2009-07-23 | 2010-02-17 | 上海大屯能源股份有限公司 | Endless rope speed regulation mechanical winch driving device used for mine |
| CN101670989A (en) * | 2009-09-25 | 2010-03-17 | 沈荣骥 | Compact-type built-in differential velocity regulating winch |
| CN102320528A (en) * | 2011-06-20 | 2012-01-18 | 康少松 | Hoisting mechanism of double-speed accelerated lowering device for crane |
| CN103883686A (en) * | 2014-03-11 | 2014-06-25 | 徐州科源液压股份有限公司 | Double-speed ratio walking speed reducer |
| CN205244272U (en) * | 2015-12-31 | 2016-05-18 | 杨崇庆 | Utilize double -brake to realize that planetary reducer of double speed work constructs |
| CN211371178U (en) * | 2019-12-10 | 2020-08-28 | 南京高精齿轮集团有限公司 | Double-speed-ratio gearbox |
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Application publication date: 20201225 |