CN102425612B - Coupling for large-sized ship low-speed electric-control diesel engine strap high-pressure oil pump - Google Patents
Coupling for large-sized ship low-speed electric-control diesel engine strap high-pressure oil pump Download PDFInfo
- Publication number
- CN102425612B CN102425612B CN201110391026.XA CN201110391026A CN102425612B CN 102425612 B CN102425612 B CN 102425612B CN 201110391026 A CN201110391026 A CN 201110391026A CN 102425612 B CN102425612 B CN 102425612B
- Authority
- CN
- China
- Prior art keywords
- live axle
- oil pump
- screw
- shearing nut
- rectangular opening
- 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.)
- Active
Links
Images
Abstract
The invention discloses a coupling for a large-sized ship low-speed electric-control diesel engine strap high-pressure oil pump, which comprises a first drive shaft and a second drive shaft, wherein the first drive shaft is connected with the second drive shaft through a special disc and a shear nut, a washer and a screw are sequentially connected with the left side end part of the first drive shaft, and the screw passes through the first drive shaft and is connected with the shear nut. Due to the adoption of the coupling, the normal running of the electric-control main engine strap high-pressure oil pump can be guaranteed, accurate and stable system oil pressure can be supplied to a main engine,the main engine is malfunction ,can be prompt wring shear nut, protection high-pressure oil pump at the same time protection main engine drive system safety, other oil pumps are free from being influenced by the malfunction of one oil pump, and the stopping of the main engine can be avoided.
Description
Technical field
The present invention relates to a kind of technical field of electric-control diesel engine band high pressure oil pump, particularly relate to a kind of for argosy the shaft coupling with low-speed electric-control diesel engine band high pressure oil pump.
Background technique
In various construction machine equipment, exist diversified connection for transmission device, for meeting different transmission demands, often there are some different structures, and the also most important thing in design problem often of a kind of suitable drive mechanism design.
Marine low speed diesel engine is the nucleus equipment of large ship, in vessel motion process, often needs a few weeks longer even continuous operation a couple of days, in whole service process, must guarantee that all parts have very high reliability and adaptability.Along with the day by day harsh requirement that international convention proposes marine diesel engine in recent years, increasing marine diesel engine is brought into use electronic control technology.
For electronic controlled diesel, its major character is to have cancelled fuel oil injection and the outlet valve transmission system that traditional mechanical transmission is controlled, and uses the switch that electrical signal is controlled fuel oil injection and outlet valve instead.Here the switch of controlling relevant valve member by electrical signal carrys out the effect of main control system high-pressure system oil to different parts, to reach, controls that fuel oil sprays and the object of outlet valve switch.From design angle, consider, be unsuitable for outside host computer system separately for high-pressure system oil arranges a set of independent pressurization system, so a set of machine band high pressure oil pump is set on main frame, to produce the hyperbaric environment of system oil.
Take 60MEC main frame as example, totally three of machine band pumps, the same driving gear driving by bent axle provides power to three machine band high pressure oil pumps power delivered coupling separately.For meeting the long stable operation of main frame, require three machine band high pressure oil pumps can not interfere with each other in running, make system oil maintain more stable pressure environment, this forces us to find a kind of safe, effective, adaptable transmission device.
Summary of the invention
The object of the invention is to overcome above-mentioned the deficiencies in the prior art, provide a kind of for argosy the shaft coupling with low-speed electric-control diesel engine band high pressure oil pump, make the operation that machine band high pressure oil pump can continous-stable, sufficiently stable system oil pressure is provided, mutual noninterference in running simultaneously, is unlikely to affect because of local fault the operation of whole system.
Based on above-mentioned purpose, technical solution of the present invention is as follows:
A kind of for argosy the shaft coupling with low-speed electric-control diesel engine band high pressure oil pump, be characterised in that its formation comprises the first live axle and the second live axle, this first live axle and the second live axle are connected to each other by Special disc and shearing nut, left end at this first live axle is provided with packing ring and screw successively, this screw runs through the first live axle, and is connected with described shearing nut.
The left end outside of described the first live axle is a circle spline, for coordinating with the driving gear of main frame; The right-hand member outside of this first live axle is provided with annulus boss, for compressing described Special disc;
Described the first shaft center is provided with ladder hole, and the left and right end diameter of this ladder hole is greater than respectively its middle part diameter, and the left end of ladder hole is for the head of retaining washer and screw; The right-hand member of ladder hole is rectangular opening, and the degree of depth of this rectangular opening and shearing nut small end thickness are suitable, and the first live axle is rotated together with shearing nut; The middle part diameter of described ladder hole is greater than the diameter of described screw rod portion;
The right-hand member inner side of described the second live axle is a spline housing, for coordinating with the transmission shaft of high pressure oil pump; The left end outside of described the second live axle is provided with annulus boss, for compressing described Special disc;
Described the second live axle left end center has a step hole and rectangular opening successively, this step hole depth and the rectangular opening degree of depth and suitable with the thickness of the large end of described shearing nut;
The right-hand member inner side of described the second live axle is a spline housing, for coordinating with the transmission shaft of high pressure oil pump; The left end outside of the second live axle is provided with annulus boss, for compressing described Special disc;
Described the second live axle left end center has step hole and rectangular opening successively, this step hole depth and the rectangular opening degree of depth and suitable with the thickness of the large end of described shearing nut, between rectangular opening and spline housing, be provided with circular hole, this circular hole is communicated with rectangular opening, and has step;
During installation, shearing nut penetrates from spline housing one side end, and the rectangle plane of the large end of shearing nut and second drives the rectangular opening in left side to coordinate, and the second live axle is rotated together with shearing nut; The thrust disc of the large end of shearing nut end is inlayed in the circular hole of the second live axle simultaneously, and is blocked by the step in circular hole, makes shearing nut apply axial tension to the second live axle.
Described Special disc is a circular thin dish, and dish both side surface scribbles respectively high abrasion coating;
The centre of described shearing nut is thin axle, and the left side of this thin axle is called small end, and right side is large end, and the external diameter of thin axle is less than the external diameter of described small end or large end;
The right-hand end of the large end of shearing nut is cylinder type thrust disc, and other shaft part both sides of shearing nut are respectively the plane of pair of parallel symmetry, for coordinating with the rectangular opening of described two live axles respectively;
Shearing nut small end end is provided with an interior threaded hole along axis centre, for described screw, fixes;
The long socket head screw of described screw one, its length and described the first live axle length are suitable.
Outside the shape size of annulus boss in the right-hand member outside of the first live axle and the left end of the second live axle, there is annulus boss shape size suitable.
The thickness of described high abrasion coating is (0.1 ± 0.05mm).
By shearing nut and screw, respectively the first live axle and the second live axle are applied to certain impacting force, the Special disc in the middle of compressing, thus between the first live axle, Special disc and the second live axle, produce certain stiction, reach the effect of transmitting torque.
For guaranteeing that the moment of torsion of shaft coupling transmission can reach user demand, after having assembled, shaft coupling needs it to carry out torsional moment test: the moment of torsion that the first live axle and the second live axle is imposed a regulation, under the effect of this moment of torsion, both and Special disc should not slide, so just can guarantee that shaft coupling is energy-conservation for the enough moments of torsion of oil pump transmission, high pressure oil pump be run well and obtain correct, stable system oil pressure.(moment of test use gets according to design user demand.）
For each oil pump is not interfered mutually, also need shaft coupling to carry out destruction test one time: equally the first live axle and the second live axle are imposed to a prescribed torque, the actual moment of torsion that twists off for shearing nut of this moment of torsion, under the effect of this prescribed torque, should there is relative sliding in two live axles and Special disc, and shearing nut should be twisted off, now the first live axle and the second live axle are free to relative movement, be equivalent to high pressure oil pump and driving gear to throw off, even if there is like this certain high pressure oil pump to break down, also can not cause the fault of whole driving mechanism, make main frame can keep running.
Compared with prior art, beneficial effect of the present invention is as follows:
1, guarantee the normal operation of automatically controlled main frame machine band high pressure oil pump, for main frame provides correct stable system, have pressure, thereby guarantee the normal operation of main frame.
2, when main frame occurs that load increases, transmission system is stuck, oil pump is stuck, when lack of lubrication or other faults, can twist off in time shearing nut, the also safety of protected host transmission system in the time of protection high pressure oil pump.
3,, for the independent failure problems of certain high pressure high pressure oil pump, its impact will only be confined to this oil pump, and can not affect other because of the fault of an oil pump, even cause Main Engine Cut-Off.
Accompanying drawing explanation
Fig. 1 be the present invention for argosy the sectional view with the shaft coupling of low-speed electric-control diesel engine band high pressure oil pump.
Fig. 2 is C portion amplification view in Fig. 1.
Fig. 3 is the sectional view of the first live axle in Fig. 1.
Fig. 4 is the sectional view of the second live axle in Fig. 1.
Fig. 5 is the sectional view of Special disc in Fig. 1.
Fig. 6 is the sectional view of shearing nut in Fig. 1.
Fig. 7 is the sectional view of screw in Fig. 1.
Fig. 8 is the sectional view of Fig. 1 middle washer.
Fig. 9 is the schematic diagram of torsional moment test or destruction test.
In figure: A-socket wrench specially adapted for it; B-fixed bearing.
Embodiment
Below in conjunction with drawings and Examples, the invention will be further elaborated, but can not limit the scope of the invention with this.
Refer to Fig. 1, Fig. 1 be the present invention for argosy the sectional view with the shaft coupling of low-speed electric-control diesel engine band high pressure oil pump, as shown in the figure, a kind of for argosy the shaft coupling with low-speed electric-control diesel engine band high pressure oil pump, comprise the first live axle 1 and the second live axle 2, this first live axle 1 and the second live axle 2 are connected to each other by Special disc 3 and shearing nut 4, left end at this first live axle 1 is connected with packing ring 6 and screw 5 in turn, this screw 5 runs through the first live axle 1, and is connected with described shearing nut 4.
Fig. 3 is the sectional view of the first live axle in Fig. 1, and as seen from the figure, the left end of the first live axle 1 outside is a circle spline, for coordinating with the driving gear of main frame; The right-hand member outside of this first live axle 1 is provided with annulus boss, for compressing described Special disc 3; Described the first live axle 1 center is provided with ladder hole, and the left and right end diameter of this ladder hole is greater than respectively its middle part diameter, and the left end of ladder hole is for the head of retaining washer 6 and screw 5; The right-hand member of ladder hole is rectangular opening, and the degree of depth of this rectangular opening and shearing nut 4 small end thickness are suitable, and the first live axle 1 is rotated together with shearing nut 4; The middle part diameter of described ladder hole is greater than the diameter of described screw rod portion.
Fig. 4 is the sectional view of the second live axle in Fig. 1, as seen from the figure,
The right-hand member inner side of described the second live axle 2 is a spline housing, for coordinating with the transmission shaft of high pressure oil pump; The left end outside of described the second live axle 2 is provided with annulus boss, for compressing described Special disc 3;
Described the second live axle 2 left end centers have a step hole and rectangular opening successively, this step hole depth and the rectangular opening degree of depth and suitable with the thickness of described shearing nut 4 large ends;
Described the second live axle 2 left end centers have step hole and rectangular opening successively, this step hole depth and the rectangular opening degree of depth and suitable with the thickness of described shearing nut 4 large ends, between rectangular opening and spline housing, be provided with circular hole, this circular hole is communicated with rectangular opening, and has step;
During installation, shearing nut 4 penetrates from spline housing one side end, and the rectangle plane of shearing nut 4 large ends coordinates with the rectangular opening in the second live axle 2 left sides, and the second live axle is rotated together with shearing nut; The thrust disc of the large end of shearing nut end is partly inlayed into the circular hole of the second live axle, and is blocked by the step in circular hole, makes shearing nut apply axial tension to the second live axle.
Outside the shape size of annulus boss in the right-hand member outside of the first live axle 1 and the left end of the second live axle 2, there is annulus boss shape size suitable.
Fig. 5 is the sectional view of Special disc in Fig. 1, and as seen from the figure, Special disc 3 is a circular thin dish, dish both side surface scribbles respectively high abrasion coating, the thickness of high abrasion coating is (0.1 ± 0.05mm), and for guaranteeing correct friction factor, high abrasion coating needs strict control.
Fig. 6 is the sectional view of shearing nut in Fig. 1, and as seen from the figure, the centre of shearing nut 4 is thin axle, and the left side of this thin axle is called small end, and right side is large end, and the external diameter of thin axle is less than the external diameter of described small end or large end; The effect of this section thin axle external diameter smaller portions is the moment that twists off of regulation shearing nut, and its external diameter calculates by the intensity of material.Whole shearing nut is except large end right-hand end is complete circular shaft (this section of circular shaft is called thrust disc), and other shaft part both sides all process the plane of pair of parallel symmetry, for coordinating with the rectangular opening of two live axles, and the relative rotation of each assembly of restriction body.Shearing nut small end end is provided with an interior threaded hole along axis centre, fixing for described screw 5.
Fig. 7 is the sectional view of screw in Fig. 1, and as shown in the figure, screw 5 is a long socket head screw, and its length and described the first live axle 1 length are suitable.Screw 5 penetrates from the left end of the first live axle 1, runs through whole the first live axle 1, and is connected with shearing nut 4.
Fig. 8 is the sectional view of Fig. 1 middle washer, and as shown in the figure, packing ring 6 pads, on the step surface of screw 5 and the first live axle 1 center hole, avoid screw to contact with step surface rigidity.
In the assembling process of shaft coupling:
1, first shearing nut small end is penetrated from splined end one side of the second live axle, until the thrust disc of shearing nut is bumped in the round platform hole of the second live axle and withstands plane.
2, Special disc is put on the annulus boss of the second live axle, then the annulus boss of the first live axle is just being placed on to the top of Special disc.
3, from the splined end of the first live axle, sequentially pack packing ring and screw into, screw is twisted as in the screw of shearing nut small end, and moment M1 tightens screw in accordance with regulations, make the first live axle and the second live axle compress middle Special disc.
After shaft coupling has been assembled like this, the first live axle, Special disc and the second live axle compress by screw and the shearing nut pulling force that moment M1 tightens rear generation in accordance with regulations, thereby have certain stiction, thereby make three relatively fixing.
When machine band high pressure oil pump runs well, the moment of torsion of shaft coupling transmission is less than the moment of torsion that maximum static friction force herein provides, and between the first live axle, Special disc and the second live axle, relative movement can not occur, normal delivery moment of torsion.
When machine band high pressure oil pump or driving gear any fault occur and load is increased, when moment of torsion increases, when driving torque is greater than the moment of torsion that maximum static friction force provides as increased to, between two live axles and Special disc, can there is relative sliding, at this moment the wear resistant coating of Special disc is destroyed, maximum static friction force reduces greatly, cannot guarantee again normal moment of torsion transmission, the side plane that now passes through shearing nut coordinates transmission with the rectangular opening of two live axles, this situation is in improper transmission, system oil pressure may fluctuate, and needs maintenance.
When driving torque continue to increase to be greater than shearing nut twist off moment time, in the middle of shearing nut, thin shaft portion can be twisted into two parts, thereby the moment of torsion of eliminating between the first live axle and the second live axle connects, both in free phases to motion state, this shaft coupling is no longer had an effect, and corresponding machine band high pressure oil pump quits work, and other oil pumps still can remain in operation, until boats and ships pull in to shore to reprocess again, and can not stop immediately.
In order to make, shaft coupling is energy-conservation can have corresponding correct action in above-mentioned several moment of torsion stages, before shaft coupling is arranged on main frame, must carry out torsional moment test to shaft coupling, and shearing nut is carried out to destruction test.
Torsional moment test:
Need a fixed bearing B, the spline of its end coordinates with the spline housing of the second live axle; Need a socket wrench specially adapted for it A, its spline housing and the first driveshaft end spline fitted.During test, the second driveshaft end of shaft coupling is inserted in the spline housing of fixed bearing B, socket wrench specially adapted for it A is enclosed within on the spline of the first driveshaft end, use special-purpose torsion to pull or other instruments apply a regulation moment M2.Regulation shaft coupling the first live axle and second live axle under the effect of this moment M2 do not relatively rotate as qualified, otherwise are defective.For the shaft coupling rotating in test, should disassemble, Special disc should renew, and checks each part.The shaft coupling that will be arranged on main frame for any one all should pass through this verification experimental verification.
Destruction test:
Use same instrument and mode in torsional moment test, the moment of torsion applying regulation is M3, and under this torsional interaction, first the first live axle and the second live axle should relatively rotate, and shearing nut should twist off.Destruction test only need to be done sampling check once or several times to the shearing nut of same batch, if frequency in sampling is more, can Special disc be installed and tests.
As can be seen from the above description, meet the various characteristics of shaft coupling, need the moment that twists off of the strict maximum static friction force of controlling Special disc and shearing nut, should be noted that following some:
1, strictly control the size of the first live axle and the second driveshaft end annulus boss, processing assurance, and do special nitriding treatment, guarantee area and the surface quality of boss top plane, thereby guarantee that boss top plane and Special disc have correct area of contact.
2, the thickness of strictly controlling Special disc surface high abrasion coating, guarantees correct friction factor.
3, according to the safety range of machine band high pressure oil pump design delivery pressure, calculate the torque range of normal transmission, thus calculate the screw-down torque M1 of screw, moment of torsion M2 that torsional moment test should be satisfied and shearing nut twist off moment M3.
4, according to twisting off moment M3, calculate the external diameter of choosing correct shearing nut material and thin shaft portion, and strictly control, guarantee that it twists off moment correct.
Claims (3)
- One kind for argosy the shaft coupling with low-speed electric-control diesel engine band high pressure oil pump, comprise the first live axle (1) and the second live axle (2), this first live axle (1) and the second live axle (2) are connected to each other by Special disc (3) and shearing nut (4), left end at this first live axle (1) is connected with packing ring (6) and screw (5) in turn, this screw (5) runs through the first live axle (1), and be connected with described shearing nut (4), it is characterized in that:The left end outside of described the first live axle (1) is a circle spline, for coordinating with the driving gear of main frame; The right-hand member outside of this first live axle (1) is provided with annulus boss, for compressing described Special disc (3);Described the first live axle (1) center is provided with ladder hole, and the left and right end diameter of this ladder hole is greater than respectively its middle part diameter, and the left end of ladder hole is for the head of retaining washer (6) and screw (5); The right-hand member of ladder hole is rectangular opening, and the degree of depth of this rectangular opening and shearing nut (4) small end thickness are suitable, and the first live axle (1) is rotated together with shearing nut (4); The middle part diameter of described ladder hole is greater than the diameter of described screw rod portion;The right-hand member inner side of described the second live axle (2) is a spline housing, for coordinating with the transmission shaft of high pressure oil pump; The left end outside of the second live axle (2) is provided with annulus boss, for compressing described Special disc (3);Described the second live axle (2) left end center has step hole and rectangular opening successively, this step hole depth and the rectangular opening degree of depth and suitable with the thickness of the large end of described shearing nut (4), between rectangular opening and spline housing, be provided with circular hole, this circular hole is communicated with rectangular opening, and has step;Described Special disc (3) is a circular thin dish, and dish both side surface scribbles respectively high abrasion coating;The centre of described shearing nut (4) is thin axle, and the left side of this thin axle is called small end, and right side is large end, and the external diameter of thin axle is less than the external diameter of described small end or large end;The right-hand end of the large end of shearing nut is cylinder type thrust disc, and other shaft part both sides of shearing nut are respectively the plane of pair of parallel symmetry, for coordinating with the rectangular opening of described two live axles respectively;Shearing nut small end end is provided with an interior threaded hole along axis centre, fixing for described screw (5);Described screw (5) is a long socket head screw, and its length and described the first live axle (1) length are suitable.
- 2. shaft coupling according to claim 1, is characterized in that, has annulus boss shape size suitable outside the shape size of annulus boss in the right-hand member of the first live axle (1) outside and the left end of the second live axle (2).
- 3. shaft coupling according to claim 1, is characterized in that, the thickness of described high abrasion coating is 0.1 ± 0.05mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110391026.XA CN102425612B (en) | 2011-12-01 | 2011-12-01 | Coupling for large-sized ship low-speed electric-control diesel engine strap high-pressure oil pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110391026.XA CN102425612B (en) | 2011-12-01 | 2011-12-01 | Coupling for large-sized ship low-speed electric-control diesel engine strap high-pressure oil pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102425612A CN102425612A (en) | 2012-04-25 |
| CN102425612B true CN102425612B (en) | 2014-03-19 |
Family
ID=45959629
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201110391026.XA Active CN102425612B (en) | 2011-12-01 | 2011-12-01 | Coupling for large-sized ship low-speed electric-control diesel engine strap high-pressure oil pump |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN102425612B (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110608227B (en) * | 2019-10-22 | 2020-10-13 | 中国北方车辆研究所 | Crawler vehicle transmission system transmission main shaft capable of improving fatigue strength life |
Family Cites Families (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5681294A (en) * | 1979-12-05 | 1981-07-03 | Nippon Seiko Kk | Main shaft device |
| GB2070735B (en) * | 1980-02-29 | 1983-04-20 | Yule & Co Ltd G H | Shaft couplings for ic engine oil pumps |
| CN2718240Y (en) * | 2003-12-03 | 2005-08-17 | 广西玉柴机器股份有限公司 | Diesel oil engine fuel pump driving device |
| CN101263308A (en) * | 2005-09-13 | 2008-09-10 | 诺伊曼尔·泰克福尔控股有限公司 | Hollow shaft and manufacturing method thereof |
| CN201190738Y (en) * | 2008-04-04 | 2009-02-04 | 隋建卫 | Straight-coupling type gear oil pump generator with coupler |
| CN201197095Y (en) * | 2008-04-22 | 2009-02-18 | 孟宪高 | Oil pump electrical machinery |
| CN101285440B (en) * | 2008-05-06 | 2011-05-11 | 奇瑞汽车股份有限公司 | High voltage oil fuel pump transmission mechanism |
| DE102010020578A1 (en) * | 2010-05-14 | 2011-11-17 | Bayerische Motoren Werke Aktiengesellschaft | Device for driving an auxiliary unit |
| CN201827259U (en) * | 2010-10-25 | 2011-05-11 | 琮伟机械（昆山）有限公司 | Coupling |
-
2011
- 2011-12-01 CN CN201110391026.XA patent/CN102425612B/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| CN102425612A (en) | 2012-04-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN102341588B (en) | Device for driving a pair of counter-rotating propellers by means of an epicyclic gear train | |
| CN104908036A (en) | Industrial robot | |
| CN102425612B (en) | Coupling for large-sized ship low-speed electric-control diesel engine strap high-pressure oil pump | |
| CN105508690B (en) | A kind of pass valve drive and its booster quick action emergency valve | |
| CN100567754C (en) | Rotatablely moving of actuation bolt directly is transferred to by the used coupling of the translation jaw of its driving | |
| CN201049421Y (en) | Vertical tightener for nut | |
| EP0016189A1 (en) | Coupling for disconnecting a motor drive and driven accessory | |
| CN103047169A (en) | Adjustable thrust structure for balancing axial force of gear | |
| CN206917958U (en) | A kind of axial flow fan with adjustable moving blades hydraulic cylinder servo control mechanism transmission device | |
| CN113280160B (en) | Detachable axial-flow check valve normally open structure | |
| CN115727149A (en) | Online disassembling and assembling tool and method for upper-mounted ball valve | |
| CN207715312U (en) | A kind of plunger pump | |
| CN202140526U (en) | Torsion limiter | |
| CN106184714A (en) | A kind of aircraft control surface loads and drift angle limits device | |
| US9970658B2 (en) | Pressure relief valve with rotating damper | |
| EP2488757A1 (en) | Underwater compressor arrangement and underwater process fluid conveying arrangement equipped therewith | |
| RU2657150C2 (en) | Device for flange connections assembly or disassembly | |
| CN205001404U (en) | A shaft coupling for steam turbine main oil pump | |
| CN105485190B (en) | Gimbal coupling with torque limiter | |
| CN211141159U (en) | Spring cable drum | |
| CN218718660U (en) | Speed reducer self preservation protects structure and speed reducer | |
| CN211920867U (en) | Balance arm of lower-mounted crane pipe | |
| CN215673268U (en) | Friction type torsion overload protection device | |
| CN216343118U (en) | Pressure relief device of high-pressure cavity in hydraulic system | |
| JP4148039B2 (en) | Reciprocating compressor |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |