CN111089124A - Mechanical full-disengaging overload protection clutch - Google Patents
Mechanical full-disengaging overload protection clutch Download PDFInfo
- Publication number
- CN111089124A CN111089124A CN201911403460.8A CN201911403460A CN111089124A CN 111089124 A CN111089124 A CN 111089124A CN 201911403460 A CN201911403460 A CN 201911403460A CN 111089124 A CN111089124 A CN 111089124A
- Authority
- CN
- China
- Prior art keywords
- overload
- clutch
- flange
- stud
- overload protection
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D43/00—Automatic clutches
- F16D43/02—Automatic clutches actuated entirely mechanically
- F16D43/20—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure
- F16D43/202—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type
- F16D43/204—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with intermediate balls or rollers
- F16D43/206—Automatic clutches actuated entirely mechanically controlled by torque, e.g. overload-release clutches, slip-clutches with means by which torque varies the clutching pressure of the ratchet type with intermediate balls or rollers moving axially between engagement and disengagement
Abstract
A mechanical full-disengagement overload protection clutch belongs to the field of clutch design. The mechanical full-disengagement overload protection clutch is characterized in that an overload element is arranged on the basis of an original clutch, when a main motor is overloaded and the borne Mn1 torque value exceeds the set overload torque limit value Mn2 of the clutch, a ball and a stud in the overload element compress a disc spring to move axially, the ball is disengaged from a rodent, and the clutch is in a disengagement state and does not retain any residual torque. The pre-installed speed measuring sensor or the axial limit switch sends an electric signal to the control system, the system automatically interrupts the power transmission of the main motor and the speed reducer, and the safety protection of the main motor, the speed reducer and the whole unit is realized.
Description
Technical Field
The invention belongs to the field of clutch design, and provides a mechanical full-disengagement overload protection clutch applied to an extruder.
Background
The extruder is an important device in the plastic product industry and has a large market share. In particular, a large-sized extrusion granulation extruder is a high-efficiency unit, is favored by petrochemical companies and raw material manufacturing plants due to high speed, high efficiency, high torque and high profit, and has incomparable superiority in plastic granulation in the petrochemical industry.
The extruder is characterized by medium load, stable load, small impact, constant screw output torque and keeping the rated torque at 60-80%; however, continuous operation and high reliability are required, for example, 8000 hours of continuous operation is required in the petrochemical industry, which puts high requirements on the design and configuration of the whole extruder unit. In order to ensure the reliability of the extruder unit, it is the objective of the extruder manufacturer to design or select a safety clutch between the main motor and the main reducer that meets the requirements of presetting the overload torque value, immediately disengaging during overload, and simply and quickly resetting.
At present, various high-quality safety clutches applied to the extruder are provided, such as a pneumatic friction clutch of DESCH, a Safeset hydraulic safety clutch of EMERSON, a mechanical shear pin clutch and the like, which have advantages and disadvantages.
Disclosure of Invention
The invention provides a mechanical full-disengagement overload protection clutch applied to an extruder, which is a novel safety clutch and is an effective guarantee for safety when a main motor and a speed reducer in the extruder are overloaded.
The technical scheme of the invention is as follows:
a mechanical full-disengagement overload protection clutch is characterized in that an overload element 11 is arranged on the basis of an original clutch, the overload element 11 is positioned between a pressure flange 4 and an element flange 2, and the overload element 11 comprises a rodent, a ball, a stud 11-1-1 and a stud compression disc spring 11-8; the rodent is arranged in the pressure flange 4, and the round ball, the stud 11-1-1 and the stud compression disc spring 11-8 are arranged in the element flange 2; wherein, the round ball is fixed at one end of the stud 11-1-1, and the other end of the stud 11-1-1 is sleeved with a stud compression disc spring 11-8; when the main motor is overloaded and the borne Mn1 torque value exceeds the set overload torque limit value Mn2 of the clutch, the ball and the stud in the overload element 11 compress the disc spring 11-8 to move axially, the ball is separated from the rodent, and the clutch is in a disengaged state.
The overload element 11 also comprises an adjusting nut 11-4, a distance bushing 19, a switch disc 20 and a countersunk screw 21; the distance bushing 19 is arranged at one end of the stud 11-1-1, the adjusting nut 11-4 is sequentially sleeved at the combination part of the distance bushing 19 and the stud 11-1-1 from outside to inside, the countersunk head screw 21 is sequentially inserted into one end of the distance bushing 19 and one end of the stud 11-1-1 from outside to inside, and the switch disc 20 is arranged at the end part of the countersunk head screw 21.
The pressure flange 4 and the element flange 2 are both provided with mark points 31, so that when the rodent and the round ball in the overload element 11 are engaged, the mark points 31 on the pressure flange 4 and the element flange 2 are aligned.
The element flange 2 has 2 conical lubricating nipples for lubricating the bearings and 2 to 4 conical lubricating nipples for lubricating the overload element 11.
The electronic signal of the clutch closes the power by two modes: 1) a limit switch: overload is identified by sensing the axial travel of the switch plate 20; 2) the rotating speed monitoring device comprises: speed sensor sensing control elements are respectively arranged on the element flange 2 and the pressure flange 4, and when the speed difference exceeds a set value, an electric signal is sent to a control system by measuring the speed difference between the element flange 2 and the pressure flange 4, so that the system automatically interrupts the power transmission of the main motor and the speed reducer.
The overload limiting torque value of the clutch is set by adjusting the prestress of the stud compression disc spring 11-8 on each overload element 11. The overload limiting torque value is realized by adjusting the distance between the shaft sleeve 1 and the top end of the adjusting nut 11-4 according to different working conditions of users.
The invention has the beneficial effects that:
(1) when the system is overloaded, the system is immediately disconnected, and the power transmission is automatically interrupted. The invention relates to a mechanical full-disengagement overload protection clutch, which transmits torque by an overload element consisting of a spherical steel ball and a disc spring between an element flange and a pressure flange, and when the torque exceeds a set torque limit value (overload), the clutch can be disengaged, a stud of the overload protection element moves axially (travels) and keeps a disengagement position, and the clutch can be freely slowed down and stopped in a disengagement state without any residual torque. The pre-installed speed measuring sensor or the axial limit switch sends an electric signal to the control system, and the system automatically interrupts the power transmission between the main motor and the speed reducer.
(2) The limit torque value is easily adjustable and linear. The overload limiting torque value can be set in an adjustable manner, each safety clutch being designed with a maximum limiting torque and a set overload limiting torque, which is set by adjusting the prestress of a belleville spring on each overload element. The overload limiting torque value can be properly increased or decreased according to different working conditions of users, and the overload limiting torque value is realized by adjusting different data of 'a' (the size 'a' is the distance between the shaft sleeve and the top end of the adjusting nut).
(3) Simple and quick reset, and can satisfy overload for many times. After the overload condition is relieved, the clutch is simply and quickly reset. Firstly, two marking points on the outer diameters of the component flange and the pressure flange are required to be aligned; the engagement can be reset by applying a certain axial force to the stud end of each overload element. The clutch can meet overload for a plurality of times.
Drawings
FIG. 1 is a clutch effect diagram of the present invention.
Fig. 2 is a diagram of the clutch structure of the present invention.
FIG. 3 is a clutch torque operating state diagram of the present invention.
FIG. 4 is a schematic illustration of the clutch of the present invention in a normal operating condition.
Fig. 5 is a diagram of the clutch disengaged state of the present invention. Wherein, (a) is a schematic diagram, and (b) is a three-dimensional perspective diagram.
Fig. 6 is a schematic of the clutch overload torque setting of the present invention.
FIG. 7 is a schematic illustration of the clutch reset engagement of the present invention. Wherein, (a) is a schematic diagram, and (b) is a three-dimensional perspective diagram.
In the figure: 1, shaft sleeve; 2, a component flange; 3, a hexagon head bolt; 4, a pressure flange; 11 an overload element; 11-1-1 stud; 11-4 adjusting the screw cap; 11-8 studs compress disc springs; 19 distance bush; 20, a switch panel; 21 countersunk head screws; 22 a convex ring; 23 cap bolts; 25 jaw-shaped rings; 26-1 flange shaft sleeve; 26-2 middle ring; 27 a set screw; 28 an elastic intermediate ring; 31 marking points; 32 set screws.
Detailed Description
The technical solution of the present invention will be further described with reference to specific examples. The structure diagram and the working principle, the presetting of the overload limiting torque value, the reset meshing and the like are as follows:
1. the mechanical full-disengagement overload protection clutch is constructed as follows, see fig. 2.
The left-end elastic coupling of the structure diagram of the mechanical full-disengagement overload protection clutch shown in figure 2 is provided with an elastomer-compensating coupling. Is composed of the following components: flange bushing 26-1, claw ring 25, elastic intermediate ring 28, convex ring 22 and cap bolt 23. The elastomer-compensating coupling compensates for shaft position deviations of the shaft ends, the maximum allowable shaft position deviation technical parameter can be provided, and if the elastic coupling operates under impact load, the size of the elastic coupling is determined according to the clutch parameter value required by design. The flange bushing 26-1 terminates in a centering ring 26-2 for supporting the jaw ring 25 in the disassembled condition. The claw ring 25 needs to be removed in the following cases: when the elastic intermediate ring 28 of the coupling is replaced, or when the motor is required to idle to check its operating characteristics; the element flange 2 has 2 conical lubricating nipples for lubricating the bearings and 2 to 4 conical lubricating nipples for lubricating the overload element 11.
2. Principle of operation
In a normal operation state, the load output torque Mn1 of the main motor is smaller than the torque limit value Mn2 set by the clutch, and the main motor drives the speed reducer to transmit the torque to the screw of the extruder, as shown in FIG. 4; when the extruder unit has a fault, such as serious damage or breakage of a screw rod or a speed reducer internal gear pair or a bearing, and the load output torque Mn1 of the main motor is greater than the torque limit Mn2 (overload) set by the clutch, torque blockage occurs, and the clutch is cut off and disengaged, which is shown in a torque diagram of FIG. 3 and a cut-off and disengaged state diagram of the clutch of FIG. 5. As shown in fig. 2, the stud 11-1-1 of the overload element 11 (see fig. 3) is moved axially (stroke) and remains disengaged. In the disengaged condition the clutch is free to slow down to a stop, leaving no residual torque. The working principle is as follows:
(1) the main motor output torque Mn1 is 9550 × P/n; wherein P is the main motor power and n is the rotation speed;
(2) the clutch-set overload limit torque value Mn2 ═ Ft × Do ═ K/2; wherein Ft is tangential force, Do is the reference circle position of the spherical steel ball, and K is the number of the spherical steel balls on the circumference;
(3) Fa-Ft tgA, where a is the integral value of the component angle of the spherical steel ball in the axial direction.
When the output torque Mn1 of the main motor is smaller than the overload limiting torque value Mn2, the clutch normally operates;
when the main motor output torque Mn1 is greater than the overload limit torque value Mn2, the clutch is disengaged.
The pre-installed speed measuring sensor or the axial limit switch sends an electric signal to the control system, and the system automatically interrupts the power transmission between the main motor and the speed reducer. The electronic signal turns off the power in the following two ways: 1) the limit switch is suitable for the design with the switch disc 20, and the limit switch senses the axial stroke of the switch disc to identify overload. 2) The rotating speed monitoring device comprises: two speed sensor induction control elements are arranged on the device and are respectively arranged on the element flange 2 and the pressure flange 4 to measure the speed difference between the element flange 2 and the pressure flange 4, an electric signal is sent to a control system when the speed difference exceeds a set value, and the system automatically interrupts the power transmission of a main motor and a speed reducer.
3. Setting of the overload torque limit Mn2
The overload limiting torque value Mn2 can be set adjustably, each safety clutch is designed with the maximum limiting torque and the overload limiting torque Mn2 agreed by the technical agreement, the overload limiting torque is set by adjusting the prestress 11-8 of the belleville spring on each overload element 11, and the setting can be adjusted according to the torque adjusting data table in the specification of the clutch, see fig. 6. The size "a" is set by the clutch according to the overload limiting torque value Mn2 agreed by the technical agreement, and the data of the size "a" can be adjusted according to the actual working condition of the user. Dimension "a" is the distance between the sleeve 1 and the top end of the adjusting nut 11-4, and the adjusting nut 11-4 in the overload element 11 is rotated to dimension "a" with an open end wrench.
4. Reset-reengage after overload
After the overload condition is removed, the clutch simply and quickly returns, see fig. 7. First, two marking holes on the outer diameters of the component flange 2 and the pressure flange 4 must be aligned; the engagement can be reset by applying a certain axial force to the stud end of each overload element 11. The clutch can meet overload for a plurality of times. The re-engagement can be performed by several different methods or manually using an appropriate tool, depending on the existing tool, installation space, etc.
Claims (10)
1. A mechanical full-disengagement overload protection clutch is characterized in that an overload element (11) is arranged on the basis of an original clutch, the overload element (11) is positioned between a pressure flange (4) and an element flange (2), and the overload element (11) comprises a rodent, a ball, a stud (11-1-1) and a stud compression disc spring (11-8); the rodent is arranged in the pressure flange (4), and the ball, the stud (11-1-1) and the stud compression disc spring (11-8) are arranged in the element flange (2); wherein, the ball is fixed at one end of the stud (11-1-1), and the other end of the stud (11-1-1) is sleeved with a stud compression disc spring (11-8); when the main motor is overloaded and the borne Mn1 torque value exceeds the set overload torque limit value Mn2 of the clutch, the ball and the stud in the overload element (11) compress the disc spring (11-8) to move axially, the ball is separated from the rodent, and the clutch is in a disengaged state.
2. The mechanical total-disengagement overload protection clutch according to claim 1, wherein the overload element (11) further comprises an adjusting nut (11-4), a distance bushing (19), a switch plate (20) and a countersunk screw (21); the distance bushing (19) is arranged at one end of the stud (11-1-1), the adjusting nut (11-4) is sequentially sleeved at the combination part of the distance bushing (19) and the stud (11-1-1) from outside to inside, the countersunk head screw (21) is sequentially inserted into one ends of the distance bushing (19) and the stud (11-1-1) from outside to inside, and the switch disc (20) is arranged at the end part of the countersunk head screw (21).
3. A mechanical total disengagement overload protection clutch according to claim 1 or 2, characterized in that the pressure flange (4) and the element flange (2) are provided with marking points (31) to ensure that the marking points (31) on the pressure flange (4) and the element flange (2) are aligned when the rodent and the spherical ball in the overload element (11) are engaged.
4. A mechanical total disconnect overload protection clutch according to claim 1 or 2, characterised in that the element flange (2) has 2 conical lubricating nipples for lubricating the bearings and 2-4 conical lubricating nipples for lubricating the overload element (11).
5. A mechanical total disconnect overload protection clutch according to claim 3, characterised in that the element flange (2) has 2 conical lubricating nipples for lubricating the bearings and 2-4 conical lubricating nipples for lubricating the overload element (11).
6. A mechanical full-disconnect overload protection clutch according to claim 1, claim 2 or claim 5, in which the electronic signal to the clutch shuts off power in two ways: 1) a limit switch: -identifying an overload by sensing the axial travel of the switching disc (20); 2) the rotating speed monitoring device comprises: speed sensor sensing control elements are respectively arranged on the element flange (2) and the pressure flange (4), and when the speed difference exceeds a set value, an electric signal is sent to a control system by measuring the speed difference between the element flange (2) and the pressure flange (4), and the system automatically interrupts the power transmission of a main motor and a speed reducer.
7. A mechanical full disconnect overload protection clutch as claimed in claim 3 in which the electronic signal to the clutch shuts off power in two ways: 1) a limit switch: -identifying an overload by sensing the axial travel of the switching disc (20); 2) the rotating speed monitoring device comprises: speed sensor sensing control elements are respectively arranged on the element flange (2) and the pressure flange (4), and when the speed difference exceeds a set value, an electric signal is sent to a control system by measuring the speed difference between the element flange (2) and the pressure flange (4), and the system automatically interrupts the power transmission of a main motor and a speed reducer.
8. The mechanical full-separation overload protection clutch according to claim 4, wherein the electronic signal of the clutch shuts off power in two ways: 1) a limit switch: -identifying an overload by sensing the axial travel of the switching disc (20); 2) the rotating speed monitoring device comprises: speed sensor sensing control elements are respectively arranged on the element flange (2) and the pressure flange (4), and when the speed difference exceeds a set value, an electric signal is sent to a control system by measuring the speed difference between the element flange (2) and the pressure flange (4), and the system automatically interrupts the power transmission of a main motor and a speed reducer.
9. A mechanical full-disconnect overload protection clutch according to claim 1, 2, 5, 7 or 8, in which the overload limiting torque value of the clutch is set by adjusting the prestress of the stud compression disc springs (11-8) on each overload element (11); according to different working conditions of users, the overload limiting torque value is realized by adjusting the distance between the shaft sleeve (1) and the top end of the adjusting nut (11-4).
10. A mechanical total release overload protection clutch according to claim 6, in which the overload limiting torque value of the clutch is set by adjusting the prestress of the stud compression disc spring (11-8) on each overload element (11); according to different working conditions of users, the overload limiting torque value is realized by adjusting the distance between the shaft sleeve (1) and the top end of the adjusting nut (11-4).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911403460.8A CN111089124A (en) | 2019-12-31 | 2019-12-31 | Mechanical full-disengaging overload protection clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201911403460.8A CN111089124A (en) | 2019-12-31 | 2019-12-31 | Mechanical full-disengaging overload protection clutch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN111089124A true CN111089124A (en) | 2020-05-01 |
Family
ID=70397751
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201911403460.8A Pending CN111089124A (en) | 2019-12-31 | 2019-12-31 | Mechanical full-disengaging overload protection clutch |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN111089124A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114526295A (en) * | 2022-02-25 | 2022-05-24 | 蜂巢传动科技河北有限公司 | Overload protection method and device for clutch, vehicle and storage medium |
| CN114962492A (en) * | 2022-06-02 | 2022-08-30 | 四川易尚天交实业有限公司 | Friction type soft starter with adjustable torque |
| WO2023066602A1 (en) * | 2021-10-20 | 2023-04-27 | Universiteit Gent | Overload clutch with joint torque and disengagement sensing |
| CN116971871A (en) * | 2023-09-22 | 2023-10-31 | 江苏凯普特动力机械股份有限公司 | Environment-friendly diesel generating set |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2303594B2 (en) * | 1972-01-31 | 1977-08-11 | Twin Disc, Inc., Racine, Wis. (V.St.A.) | TORQUE LIMITING CLUTCH |
| DE3402860A1 (en) * | 1984-01-27 | 1985-08-01 | Chr. Mayr GmbH + Co KG, 8951 Mauerstetten | OVERLOAD ELEMENT FOR TORQUE COUPLINGS |
| JPS631822A (en) * | 1986-06-20 | 1988-01-06 | Takahiro Kogyo Kk | Encapsulated liquid torque limiter |
| GB2165899B (en) * | 1984-10-12 | 1988-06-08 | Masao Fukumoto | Coupling torque limiter |
| CN2888169Y (en) * | 2006-01-20 | 2007-04-11 | 姜其平 | Adjustable mechanical transmission coupling device with overload protection function |
| CN201177020Y (en) * | 2008-03-27 | 2009-01-07 | 锦州万得包装机械有限公司 | Safety clutch |
| CN201587416U (en) * | 2010-01-19 | 2010-09-22 | 西安奥瑞德信号电气有限公司 | Ball coupler |
| CN103846924A (en) * | 2013-08-14 | 2014-06-11 | 中国科学院合肥物质科学研究院 | Electromechanical connecting interface of robot modularized joint with adjustable rigidity |
| CN104632934A (en) * | 2014-12-10 | 2015-05-20 | 东南大学 | Servo turret head overload protection device |
| CN105460823A (en) * | 2015-12-10 | 2016-04-06 | 中国船舶重工集团公司第七一三研究所 | Force closing type feedback torque limiting device |
| CN108884884A (en) * | 2016-04-07 | 2018-11-23 | 福伊特专利有限公司 | Torque limit shaft coupling |
| DE202019003203U1 (en) * | 2019-07-30 | 2019-09-04 | Chr. Mayr Gmbh + Co. Kg | Isolation overload clutch with modular design |
-
2019
- 2019-12-31 CN CN201911403460.8A patent/CN111089124A/en active Pending
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2303594B2 (en) * | 1972-01-31 | 1977-08-11 | Twin Disc, Inc., Racine, Wis. (V.St.A.) | TORQUE LIMITING CLUTCH |
| DE3402860A1 (en) * | 1984-01-27 | 1985-08-01 | Chr. Mayr GmbH + Co KG, 8951 Mauerstetten | OVERLOAD ELEMENT FOR TORQUE COUPLINGS |
| GB2165899B (en) * | 1984-10-12 | 1988-06-08 | Masao Fukumoto | Coupling torque limiter |
| JPS631822A (en) * | 1986-06-20 | 1988-01-06 | Takahiro Kogyo Kk | Encapsulated liquid torque limiter |
| CN2888169Y (en) * | 2006-01-20 | 2007-04-11 | 姜其平 | Adjustable mechanical transmission coupling device with overload protection function |
| CN201177020Y (en) * | 2008-03-27 | 2009-01-07 | 锦州万得包装机械有限公司 | Safety clutch |
| CN201587416U (en) * | 2010-01-19 | 2010-09-22 | 西安奥瑞德信号电气有限公司 | Ball coupler |
| CN103846924A (en) * | 2013-08-14 | 2014-06-11 | 中国科学院合肥物质科学研究院 | Electromechanical connecting interface of robot modularized joint with adjustable rigidity |
| CN104632934A (en) * | 2014-12-10 | 2015-05-20 | 东南大学 | Servo turret head overload protection device |
| CN105460823A (en) * | 2015-12-10 | 2016-04-06 | 中国船舶重工集团公司第七一三研究所 | Force closing type feedback torque limiting device |
| CN108884884A (en) * | 2016-04-07 | 2018-11-23 | 福伊特专利有限公司 | Torque limit shaft coupling |
| DE202019003203U1 (en) * | 2019-07-30 | 2019-09-04 | Chr. Mayr Gmbh + Co. Kg | Isolation overload clutch with modular design |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2023066602A1 (en) * | 2021-10-20 | 2023-04-27 | Universiteit Gent | Overload clutch with joint torque and disengagement sensing |
| CN114526295A (en) * | 2022-02-25 | 2022-05-24 | 蜂巢传动科技河北有限公司 | Overload protection method and device for clutch, vehicle and storage medium |
| CN114526295B (en) * | 2022-02-25 | 2023-10-10 | 蜂巢传动科技河北有限公司 | Overload protection method and device for clutch, vehicle and storage medium |
| CN114962492A (en) * | 2022-06-02 | 2022-08-30 | 四川易尚天交实业有限公司 | Friction type soft starter with adjustable torque |
| CN116971871A (en) * | 2023-09-22 | 2023-10-31 | 江苏凯普特动力机械股份有限公司 | Environment-friendly diesel generating set |
| CN116971871B (en) * | 2023-09-22 | 2023-12-26 | 江苏凯普特动力机械股份有限公司 | Environment-friendly diesel generating set |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN111089124A (en) | Mechanical full-disengaging overload protection clutch | |
| CN200952536Y (en) | Friction type overload limit torque coupling | |
| CN106984995B (en) | Numerically-controlled slide machining overload protective device | |
| CN204164219U (en) | A kind of step-by-step movement reseting torque limiter | |
| CN104842372A (en) | Overload protection device for joint of humanoid robot | |
| CN102182765B (en) | Steel ball dropped type torque limiter | |
| CN201730975U (en) | Coupler safety overload protective device | |
| CN101813146B (en) | Coupling braking load limiter | |
| CN105485197A (en) | Torque limiter provided with elastic membrane coupling | |
| CN212804002U (en) | Torque monitoring clutch of cigarette making machine | |
| CN204493501U (en) | Novel steel ball limited torque device | |
| CN103671608A (en) | Centre type torque overload protection device | |
| CN202971643U (en) | Novel movable fixed torque coupling | |
| CN202926910U (en) | A steel ball-type force-limiting safety coupling | |
| US6059087A (en) | Torque limiting clutch | |
| CN203627578U (en) | Centre type torque overload protection device | |
| CN202001516U (en) | Steel ball disengaging torque limiter | |
| CN111878517A (en) | Bidirectional adjustment friction coupling for electric switch machine | |
| CN210318250U (en) | Conical surface friction type torque limiter | |
| CN102854007A (en) | Dynamic test stand of backstop | |
| CN213393225U (en) | Torque overload protector | |
| CN203836137U (en) | Gear | |
| CN109973535B (en) | Automatic clutch protection diaphragm coupler for torque overload | |
| CN205479008U (en) | Safety clutch | |
| CN212407369U (en) | Take threshold value moment of torsion speed reducer |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20200501 |
|
| RJ01 | Rejection of invention patent application after publication |