CN201367324Y - Capstan shift clutch - Google Patents
Capstan shift clutch Download PDFInfo
- Publication number
- CN201367324Y CN201367324Y CNU2009201150316U CN200920115031U CN201367324Y CN 201367324 Y CN201367324 Y CN 201367324Y CN U2009201150316 U CNU2009201150316 U CN U2009201150316U CN 200920115031 U CN200920115031 U CN 200920115031U CN 201367324 Y CN201367324 Y CN 201367324Y
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- CN
- China
- Prior art keywords
- clutch
- cam
- capstan
- shift
- axle
- 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.)
- Expired - Lifetime
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Abstract
The utility model discloses a capstan shift clutch, which comprises a shell and a handle, wherein a clutch cam gear shaft is arranged in the shell; a shift cam shaft and a shift clutch shaft are penetrated and connected in the clutch cam gear shaft; the clutch cam gear shaft and the cam curved surface of the shift cam shaft are sequentially linked and fitted; a clutch resetting spring is arranged between the clutch cam gear shaft and the shell; a shift resetting spring is arranged between the shift cam shaft and the shell; a locating component that can slide on the cam curved surface is arranged on the shift clutch shaft; and the handle is fixedly connected with the shift clutch shaft. The capstan shift clutch has the advantages of simple and convenient operation and reliable working; under the conditions that the function of a capstan is not reduced and the weight-pull ratio of the capstan is not decreased, the dual speed capability is enhanced; the clutch and shift are integrated, namely, the shift and clutch commonly use one operating handle; the two actions caused by a shift clutch component are organically combined with a speed reducer, and the gears of the speed reducer of the capstan can be automatically separated and meshed; therefore, the operation is extremely convenient and reliable, the structure is compact, the failure rate is low, and the service life is long.
Description
Technical field
The utility model relates to a kind of capstan winch shift clutch.
Background technology
The capstan winch kind is a lot, the special-purpose capstan winch of all kinds of leisure cross-country car Hauler for ship, all kinds of special engineered operation capstan winch, various armies special purpose capstan winch and other every profession and trade etc. is arranged, fishery and oil, exploitation of mineral resources etc. are herded in be widely used in lying fallow cross-country, engineering rescue, metallurgy, exploration, woods, and wherein lying fallow cross-country is the capstan winch principal market.At present domestic and international capstan winch is usually by motor (motor, HM Hydraulic Motor, air motor etc.), drum brake, retarder, power-transfer clutch, controller, several most of compositions such as steel rope and some corresponding accessories, substantially can satisfy the requirement of various operating modes, but can not adapt to the requirement of more and more higher living standard and operating mode technology, increasing user proposes higher requirement to capstan speed, on the main application market of the cross-country capstan winch of leisure, often the propulsion source of capstan winch has significant limitation, and the unique method that solves the capstan speed problem like this makes that exactly winch reductor has speed threshold.It is that the double speed capstan winch that the military is equipped with has similar functions that U.S. Milker (miniature cross-country car capstan winch maker of U.S. army) and German Rotzer (the military capstan winch equipment in various countries, whole world maker) two companies are only arranged in the world at present, German company double speed capstan winch has only height and bottom gear, do not have power-transfer clutch, do not have the artificial rope function of freely putting; U.S. army's double speed capstan winch power-transfer clutch places two different positions of winch reductor with shift handle, must two handles be used and just can obtain at a high speed; When top gear was worked, power-transfer clutch must be at disengaged position, and not throw off winch reductor be lock-out state in clutch if gear placed at a high speed, and misoperation is easy to cause retarder or system failure.
(volume) weight of capstan winch and the pulling force of capstan winch are than the important indicator that is a capstan winch, and be particularly important when various mini locomotives and cross-country rescue work.Present 5000 pounds of (below two tons) capstan winches producing in the world, its ratio is up to 400 times, and 5000 pounds to 12000 pounds its ratios of capstan winch are up to 150 times, and 10000 pounds of ratios to 20000 pounds of capstan winches reach more than 100 times.With its so little volume and weight requirement, accomplish that capstan winch promptly has clutch and manually puts the rope function, the gear that also needs simultaneously to slow down switches, and the also necessary standard-required that guarantees of the load-carrying capacity of capstan winch, is not an easy thing.The mode that U.S. Milker takes is the brake function that has removed capstan winch, capstan winch has been made the one-level deceleration, and top gear is taked by motor from connecing head roll, obviously such its capstan winch of scheme can only be finished some simple rescue works, its double speed function adopts the another one shift handle simultaneously, and to be used with clutch handle, use very inconvenient.
The utility model content
The purpose of this utility model is to provide capstan crab gear shift sleeve, can effectively solve existing capstan winch needs shift handle and clutch handle to be used simultaneously when gearshift and clutch operation, not only operates the problem that inconvenience and misoperation are easy to cause retarder or system failure.
In order to solve the problems of the technologies described above, the utility model adopts following technical scheme: capstan crab gear shift sleeve, comprise housing and handle, it is characterized in that: be provided with clutch cam tooth axle in the housing, cross-under has shifting cam axle and gearshift clutch shaft in the clutch cam tooth axle, the match that links in proper order of cam curved surface on clutch cam tooth axle and the shifting cam axle, be provided with the clutch retracing spring between clutch cam tooth axle and the housing, be provided with the gearshift retracing spring between shifting cam axle and the housing, the gearshift clutch shaft is provided with the positioning element that slides on cam curved surface, handle captive joint gearshift clutch shaft.
Further, positioning element adopts locating dowel pin, the locating dowel pin bottom is fixedly connected in the gearshift clutch shaft, the locating dowel pin top exceeds the shift clutch outer wall and forms projection, the bossing of locating dowel pin props up on the cam curved surface of clutch cam tooth axle and shifting cam axle and slides, and the locating dowel pin bottom is fixed in the gearshift clutch shaft, and the motion process of locating dowel pin is vertical mutually with itself, be difficult for making locating dowel pin to produce and slide reliable operation.
Further, clutch cam tooth axle is provided with cam curved surface I, the shifting cam axle is provided with cam curved surface II, also be provided with the circle ring surface that joins with cam curved surface II on the shifting cam axle, circle ring surface is corresponding with the position of cam curved surface I, when locating dowel pin its circle ring surface on the shifting cam axle when the cam curved surface 1 of clutch cam tooth axle slides slides, realize clutch, when locating dowel pin is realized gearshift when the cam curved surface II of shifting cam axle slides, clutch and shift process unite two into one, easy and simple to handle reliable, compact conformation.
Preferably, cam curved surface I, cam curved surface II and circle ring surface are 1/4 circular arc, and each curved surface is made easy, and handle rotation radian is little.
Preferably, clutch cam tooth axle is provided with the ring-type draw-in groove, clutch retracing spring one end penetrates in the ring-type draw-in groove and props up bottom land, the clutch retracing spring other end props up inner walls, the clutch retracing spring embeds in the ring-type draw-in groove, can prevent that the clutch retracing spring from radially deformation taking place, displacement takes place and influence the normal operation of manual transmission.
Further, shifting cam axle inwall is provided with a ladder radially, gearshift retracing spring one end props up radially ladder bottom, the gearshift retracing spring other end props up inner walls, when the assembling of shifting cam axle and shift clutch is finished, the gearshift retracing spring is equivalent to embed in the draw-in groove that ladder radially and gearshift clutch shaft outer wall form, and the retracing spring that can prevent from equally to shift gears radially deformation takes place, is shifted, the normal operation of assurance manual transmission.
Further, the shifting cam shaft end is provided with surface bearing, after shift clutch and retarder assembling, can reduce the friction between shift lock plate and the shifting cam axle, guarantees normal operation and service life.
Further, handle guarantees can not produce relative rotation between handle and the gearshift clutch shaft by flathead screw captive joint gearshift clutch shaft, and is fixing reliable.
The utility model is owing to adopted technique scheme, easy and simple to handle, reliable operation, this capstan crab gear shift sleeve is in the function that does not reduce capstan winch, do not reduce under the situation of weight pulling force ratio of capstan winch yet, increase the double speed function, clutch and gearshift unite two into one, i.e. gearshift and the shared operating handle of clutch, two actions and retarder that reducer structure will shift gears that clutch component produces combine, and each associated gear of retarder was separated automatically under the effect of spring and is made retarder produce a big retarding with engagement to compare station when each gear switched, a neutral position, a little reduction ratio station, making only needs operating handle is placed corresponding top gear when gearshift clutch operation, neutral or bottom gear position, the winch reductor gear will separate automatically with the engagement, operate extremely convenient and reliable, compact conformation, fault rate is hanged down long service life, can promote the use of in the various winch reductors.
Description of drawings
The utility model is described in further detail below in conjunction with accompanying drawing:
Fig. 1 is the structural representation of the utility model capstan crab gear shift sleeve;
Fig. 2 is the structural representation of clutch cam tooth axle in the utility model;
Fig. 3 is the cutaway view of clutch cam tooth axle;
Fig. 4 is the structural representation of shifting cam axle in the utility model;
Fig. 5 is the front view of shifting cam axle;
Fig. 6 is the birds-eye view of Fig. 5;
Fig. 7 is the birds-eye view of Fig. 6;
Fig. 8 is the exploded view of shift clutch in conjunction with retarder;
Fig. 9 is the structural representation of sun wheel in the retarder;
Figure 10 is the structural representation of clutch gear ring in the retarder;
Figure 11 is the structural representation of output stage satellite gear in the retarder;
Figure 12 is the structural representation of input stage satellite gear in the retarder;
Figure 13 is three kinds of view of shift clutch handle;
Cutaway view when Figure 14 is in the state I bottom gear for handle among Figure 13.
The specific embodiment
Extremely shown in Figure 7 as Fig. 1, be the utility model capstan crab gear shift sleeve, comprise housing 1 and handle 2, be provided with clutch cam tooth axle 3 in the housing 1, cross-under have shifting cam axle 4 and gearshift clutch shaft 5 in the clutch cam tooth axle 3, the match that links in proper order of the cam curved surface on clutch cam tooth axle 3 and the shifting cam axle 4.Clutch cam tooth axle 3 is provided with cam curved surface I32, shifting cam axle 4 is provided with cam curved surface II42, also be provided with the circle ring surface 43 that joins with cam curved surface II42 on the shifting cam axle 4, circle ring surface 43 is corresponding with the position of cam curved surface I32, and cam curved surface I32, cam curved surface II42 and circle ring surface 43 are 1/4 circular arc.Be provided with clutch retracing spring 31 between clutch cam tooth axle 3 and the housing 1, clutch cam tooth axle 3 is provided with ring-type draw-in groove 33, and clutch retracing spring 31 1 ends penetrate in the ring-type draw-in groove 33 and prop up bottom land, and clutch retracing spring 31 other ends prop up housing 1 inwall.Be provided with gearshift retracing spring 41 between shifting cam axle 4 and the housing 1, shifting cam axle 4 inwalls are provided with a ladder 44 radially, gearshift retracing spring 41 1 ends prop up radially ladder 44 bottoms, and gearshift retracing spring 41 other ends prop up housing 1 inwall, and shifting cam axle 4 ends are provided with surface bearing 45.Gearshift clutch shaft 5 is provided with the positioning element that slides on cam curved surface, handle 2 is by flathead screw 21 captive joints gearshift clutch shaft 5.Positioning element adopts locating dowel pin 51, locating dowel pin 51 bottoms are fixedly connected in the gearshift clutch shaft 5, locating dowel pin 51 tops exceed the shift clutch outer wall and form projection 52, and projection 52 parts of locating dowel pin 51 prop up on the cam curved surface of clutch cam tooth axle 3 and shifting cam axle 4 and slide.Projection 52 parts of locating dowel pin 51 are passed the cam curved surface I32 that props up clutch cam tooth axle 3 behind the cam curved surface II42 of shifting cam axle 4, circle ring surface 43 is corresponding with the position of cam curved surface I32, when projection 52 parts of locating dowel pin 51 are slided on cam curved surface I32, the circle ring surface 43 of projection 52 parts of cooresponding locating dowel pin 51 on shifting cam axle 4 slides, clutch cam tooth axle 3 and shifting cam axle 4 can independently separately carry out respectively, also can link successively.
To shown in Figure 14, retarder comprises sun wheel 6, clutch gear ring 7, output stage satellite gear 8 and the input stage satellite gear 9 of input as Fig. 8, and sun wheel 6 cross-under are in clutch gear ring 7, output stage satellite gear 8 and input stage satellite gear 9.Sun wheel 6 is provided with low speed tooth 61 and high speed tooth 62.Be provided with primary annulus 71 in the clutch gear ring 7, clutch cam tooth axle 3 can mesh with primary annulus 71.Output stage satellite gear 8 comprises transmission gear I81, transmission gear II82 and drive link I83, and transmission gear II82 drives transmission gear I81 by drive link I83 and rotates.Input stage satellite gear 9 comprises transmission gear III91, transmission gear IV92, drive link II93 and shift lock plate 94, transmission gear III91 and primary annulus 71 engagements, drive link II93 cross-under is in shift lock plate 94, be provided with shift lock spring 95 between drive link II93 and the shift lock plate 94, be provided with in the shift lock plate 94 and sun wheel 6 high speed teeth 62 cooresponding internal tooths 96, transmission gear III91 drives shift lock plate 94 by drive link II93 and transmission gear IV92 rotates.
As shown in figure 14, working process is as follows when retarder is in bottom gear: drive transmission gear III91 as the low speed tooth 61 of the sun wheel 6 of input end and rotate, transmission gear III91 and primary annulus 71 engagements realize the one-level deceleration, transmission gear III91 drives transmission gear IV92 rotation by drive link II93 and shift lock plate 94 rotates, transmission gear IV92 and transmission gear I81 engagement drive its rotation, transmission gear I81 drives transmission gear II82 by drive link I83 and rotates realization output, because the one-level by satellite gear is slowed down, be output as bottom gear this moment.Shift lock plate 94 contacts with the surface bearing 45 of shifting cam axle 4 and rotates, this moment since projection 52 parts of locating dowel pin 51 to the position-limiting action of clutch cam tooth axle 3 and shifting cam axle 4, shift lock spring 95 is in compressive state.
When turning handle 2 during to state I I neutral gear position as shown in figure 14, projection 52 parts of locating dowel pin 51 are slided on the cam curved surface I32 of clutch cam tooth axle 3, promoting clutch cam tooth axle 3 moves right, thereby the external tooth 34 of clutch cam tooth axle 3 and primary annulus 71 are broken away from, simultaneously projection 52 parts of locating dowel pin 51 slide into the junction with cam curved surface II42 from the end of the circle ring surface 43 of shifting cam axle 4, this moment since projection 52 parts of locating dowel pin 51 to the position-limiting action of gearshift camshaft 4, shift lock spring 95 still is in compressive state.
When being rotated further handle 2 to state I II top gear position as shown in figure 14, projection 52 parts of locating dowel pin 51 are slided on the cam curved surface II42 of shifting cam axle 4, promoting shifting cam axle 4 moves right, shift lock plate 94 promoted shift lock plate 94 and moved right under the restoring force effect of shift lock spring 95 this moment, make the internal tooth 96 of shift lock plate 94 and high speed tooth 62 engagements of sun wheel 6, high speed tooth 62 directly drives shift lock plate 94 and rotates; Shift lock plate 94 drives transmission gear IV92 by drive link II93 and rotates, transmission gear IV92 is by 8 outputs of output stage satellite gear, make the satellite gear at the corresponding levels of retarder lose out deceleration effort and directly export with sun wheel 6, thereby change the retarder reduction ratio, make retarder have top gear.
The backward rotation handle has realized that from state I II to state I I retarder throws off from the clutch of high speed gear, turning handle is to position I again, retarder satellite gear at the corresponding levels produces deceleration effort under the effect of two retracing springs, make the retarder reduction ratio increase one-level, forms the bottom gear of retarder.Can certainly directly move handle to position III from position I realizes switching from low speed to high speed; Otherwise, directly move handle to position I from position III and realize from switching to low speed at a high speed.The utility model shift clutch increases the double speed function, and clutch and gearshift unite two into one, and compact conformation, easy operation, reliable operation can be applicable in the various winch reductors.
Claims (8)
1, capstan crab gear shift sleeve, comprise housing (1) and handle (2), it is characterized in that: be provided with clutch cam tooth axle (3) in the described housing (1), the interior cross-under of clutch cam tooth axle (3) has shifting cam axle (4) and gearshift clutch shaft (5), the match that links in proper order of cam curved surface on described clutch cam tooth axle (3) and the shifting cam axle (4), be provided with clutch retracing spring (31) between described clutch cam tooth axle (3) and the housing (1), be provided with gearshift retracing spring (41) between described shifting cam axle (4) and the housing (1), described gearshift clutch shaft (5) is provided with the positioning element that slides on cam curved surface, described handle (2) captive joint gearshift clutch shaft (5).
2, capstan crab gear shift sleeve according to claim 1, it is characterized in that: described positioning element adopts locating dowel pin (51), described locating dowel pin (51) bottom is fixedly connected in the gearshift clutch shaft (5), described locating dowel pin (51) top exceeds the shift clutch outer wall and forms projection (52), and the projection (52) of described locating dowel pin (51) part props up on the cam curved surface of clutch cam tooth axle (3) and shifting cam axle (4) and slides.
3, capstan crab gear shift sleeve according to claim 1 and 2, it is characterized in that: described clutch cam tooth axle (3) is provided with cam curved surface I (32), described shifting cam axle (4) is provided with cam curved surface II (42), also be provided with the circle ring surface (43) that joins with cam curved surface II (42) on the described shifting cam axle (4), described circle ring surface (43) is corresponding with the position of cam curved surface I (32).
4, capstan crab gear shift sleeve according to claim 3 is characterized in that: described cam curved surface I (32), cam curved surface II (42) and circle ring surface (43) are 1/4 circular arc.
5, capstan crab gear shift sleeve according to claim 1, it is characterized in that: described clutch cam tooth axle (3) is provided with ring-type draw-in groove (33), described clutch retracing spring (31) one ends penetrate in the ring-type draw-in groove (33) and prop up bottom land, and described clutch retracing spring (31) other end props up housing (1) inwall.
6, capstan crab gear shift sleeve according to claim 1 or 5, it is characterized in that: described shifting cam axle (4) inwall is provided with a ladder (44) radially, described gearshift retracing spring (41) one ends prop up radially ladder (44) bottom, and described gearshift retracing spring (41) other end props up housing (1) inwall.
7, capstan crab gear shift sleeve according to claim 1 is characterized in that: described shifting cam axle (4) end is provided with surface bearing (45).
8, capstan crab gear shift sleeve according to claim 1 is characterized in that: described handle (2) is by flathead screw (21) captive joint gearshift clutch shaft (5).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2009201150316U CN201367324Y (en) | 2009-03-06 | 2009-03-06 | Capstan shift clutch |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2009201150316U CN201367324Y (en) | 2009-03-06 | 2009-03-06 | Capstan shift clutch |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201367324Y true CN201367324Y (en) | 2009-12-23 |
Family
ID=41486219
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2009201150316U Expired - Lifetime CN201367324Y (en) | 2009-03-06 | 2009-03-06 | Capstan shift clutch |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN201367324Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105621300A (en) * | 2016-03-03 | 2016-06-01 | 宁波联达绞盘有限公司 | Double-speed electric capstan and use method thereof |
| CN105621299A (en) * | 2016-03-04 | 2016-06-01 | 宁波联达绞盘有限公司 | Electric double-speed winch and working method thereof |
-
2009
- 2009-03-06 CN CNU2009201150316U patent/CN201367324Y/en not_active Expired - Lifetime
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105621300A (en) * | 2016-03-03 | 2016-06-01 | 宁波联达绞盘有限公司 | Double-speed electric capstan and use method thereof |
| CN105621300B (en) * | 2016-03-03 | 2017-12-12 | 宁波联达绞盘有限公司 | Double-speed electric winch and its application method |
| CN105621299A (en) * | 2016-03-04 | 2016-06-01 | 宁波联达绞盘有限公司 | Electric double-speed winch and working method thereof |
| CN105621299B (en) * | 2016-03-04 | 2017-10-13 | 宁波联达绞盘有限公司 | Electronic double speed capstan winch and its method of work |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20091223 Effective date of abandoning: 20090306 |