CN210343568U - Clutch device for starting engine and engine - Google Patents
Clutch device for starting engine and engine Download PDFInfo
- Publication number
- CN210343568U CN210343568U CN201920543114.9U CN201920543114U CN210343568U CN 210343568 U CN210343568 U CN 210343568U CN 201920543114 U CN201920543114 U CN 201920543114U CN 210343568 U CN210343568 U CN 210343568U
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- engine
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- starting
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Abstract
The utility model discloses a clutch device and an engine for starting the engine, which comprises a clutch gear meshing pair, wherein the clutch gear meshing pair comprises a driving clutch gear and a driven clutch gear, and the driving clutch gear is arranged on a clutch gear shaft through the transmission fit of a screw pair; the utility model is used for the starting system avoids the recoil direct action that the engine reversal brought to start transmission system, avoids the return to disturb to thoroughly solve the part damage problem that the recoil that the engine reversal brought leads to, whole starting system simple structure is compact and improve foot system's stress state, not only can avoid the recoil, can also smoothly separate or mesh, extension system life reduces use and maintenance cost.
Description
Technical Field
The utility model relates to an engine part, in particular to an engaging and disengaging gear and engine for engine start.
Background
For an engine, the engine is started by electricity in a more commonly adopted starting mode, and a starting motor is utilized to drive a crankshaft to rotate and transmit torque to the engine, so that the engine is started. In the engine starting system in the prior art, in order to ensure that the started engine runs normally and does not drag a starting motor and start a transmission system to run, an overrunning clutch (one-way clutch) is arranged on a transmission chain. However, when the engine is used for a load-carrying vehicle, the problem of engine reverse rotation caused by vehicle flameout can occur in a specific occasion, when the engine rotates reversely, the rotating speed of a crankshaft is transmitted to a starter motor through an overrunning clutch (a one-way clutch), the starter motor generates a sign of large rotating speed due to the large transmission ratio (the transmission ratio is about 6.2) of the electric starting system, the one-way clutch bears large impact load, the one-way clutch is easy to damage, and meanwhile, the electric starting system can be impacted disadvantageously. The engine stalls and recoils, which causes the slip or locking problem of the isolator in a short period (one month of engine use), and the isolator fails.
Therefore, there is a need for an improvement of the existing engine starting system, when the engine is used in a load-carrying vehicle, under the condition of the kick caused by the flameout and reverse rotation of the engine, the kick of the electric starting system is not generated, the service life of the system is prolonged, the use and maintenance cost is saved, the structure is optimized, and the cost is reduced.
SUMMERY OF THE UTILITY MODEL
In view of this, the utility model provides an engine starting system and engine, when the engine was used for load vehicle, under the recoil condition that the engine flame-out reversal formed, can not form the recoil to electric starting system, the life of extension system to use and maintenance cost are practiced thrift, and optimized structure reduces self cost simultaneously.
The utility model discloses a clutch device for engine starting, which comprises a clutch gear meshing pair arranged on an engine starting transmission chain;
the clutch gear meshing pair comprises a driving clutch gear and a driven clutch gear, and the driving clutch gear is arranged on a clutch gear shaft in a transmission fit manner through a spiral pair; when the clutch gear shaft is started, the driving clutch gear is driven by the spiral pair to move axially to be in meshed transmission with the driven clutch gear when the clutch gear shaft rotates, and after the starting is finished, the driving clutch gear is driven to return and is separated from the driven clutch gear;
the helix angle of the helix pair ensures that the helix pair does not have self-locking capability;
the gear pair formed by the driving clutch gear and the driven clutch gear can be located at any position of a transmission chain of a starting transmission system theoretically and can play a role in disconnecting reverse rotation transmission, but in order to reduce impact on components in actual use, the gear pair is located at the rear end of the output of starting power as far as possible and is close to a crankshaft of an engine;
the rotation direction of the spiral pair is based on the requirement of meshing to propel the driving clutch gear to move to the driven clutch gear when the clutch gear shaft rotates, and the details are not repeated;
in the structure, when the electric starting is carried out, the starting motor inputs power into the starting transmission system so that the power is input to the clutch gear shaft, the clutch gear shaft drives the driving clutch gear to axially move through the screw pair to be meshed with the driven clutch gear while rotating, so that the starting power is transmitted to the engine crankshaft (the transmission to the engine crankshaft is realized in various modes and can be realized through gears, direct connection or other intermediate components), and the starting is realized; after the engine is started, the starting motor is stopped, the engine runs power and returns back to drive the driven clutch gear to rotate, so that the driving clutch gear is driven to rotate, the engine returns along the axial direction of the clutch gear shaft under the action of a spiral pair, the transmission chain is disengaged and disconnected, and at the moment, the engine is flamed out and reversely rotated, so that no influence is caused on the starting of a transmission system; of course, if the active clutch gear is provided with an active return, the effect of disengaging the engagement is better.
Furthermore, the driving clutch gear is provided with a return pretightening force, and the return pretightening force has a tendency of separating the driving clutch gear from the driven clutch gear; the direction of the return pretightening force is towards the direction of separating the two gears, the active clutch gear is returned, the return pretightening force helps the active clutch gear to return by combining the setting of the helix angle, a stable separation structure is formed, the interference generated during the operation is avoided, and the whole starting system is protected from being impacted.
Furthermore, the driving clutch gear is provided with a friction piece, the friction piece is used for forming friction force with the driving clutch gear, and the friction piece is arranged for forming friction on the driving clutch gear and has certain torque so as to ensure that the driving clutch gear cannot follow up easily when the clutch gear shaft rotates, thereby ensuring smooth clutch; the friction member may be in various forms, such as an elastic friction member, which is fixedly disposed with respect to a fixed member such as a case, and which causes a set rotational resistance to the driving clutch gear.
Furthermore, the helix angle of the helix pair enables the helix pair not to have self-locking capability, the helix pair is formed by helix fit, and whether the helix fit can be self-locked or not has a direct relation with the helix angle; in the structure, parameters of a helix angle are controlled, so that the helix pair can not be self-locked, the return of the active clutch gear after the completion of starting is facilitated, and the disengagement is ensured to be thorough, and the starting system including a starting motor is prevented from being impacted when an engine rotates reversely.
Furthermore, the spiral pair is formed by matching an inner spiral of the driving clutch gear with an outer spiral of the clutch gear shaft, and the return pretightening force is applied by a return spring which is sleeved outside an extending shaft section of the clutch gear shaft, one end of the return pretightening force abuts against the driving clutch gear, and the other end of the return pretightening force is axially fixed relative to the clutch gear shaft; the end part of the return spring is axially fixed by a limiting piece fixed on the clutch gear shaft to abut against the end part of the return spring; as shown in the figure, the clutch driving gear is close to the starting power input gear and is arranged on the clutch gear shaft through the spiral pair, the return spring is sleeved at the far end of the clutch gear shaft, the driven clutch gear is located on the other side, opposite to the starting power input gear, of the driving clutch gear, the whole structure is compact, the arrangement is reasonable, and for the driving clutch gear, the structure does not need to be provided with a limiting part which is prevented from being disengaged independently.
Furthermore, the friction piece is a spring friction piece, a spring friction groove is formed in the excircle of the active clutch gear, and the spring friction piece is provided with a fixed end with a set pre-tightening force, embedded in the spring friction groove and relatively fixed when extending out of the spring friction groove; the spring friction piece adjusts a proper pretightening force for applying a friction force to the active clutch gear, of course, the spring should have a fixed end for supporting the generation of the friction force, and the fixed end can be fixed at a specific position of the engine case according to the installation requirement, and will not be described herein again.
Furthermore, the clutch gear shaft is provided with a starting power input gear in a transmission fit mode, and the clutch gear shaft is generally integrally formed, simple in structure and convenient to install; the driven clutch gear is used for driving and directly connecting to a magneto rotor, so that power is transmitted to an engine crankshaft, a one-way clutch is removed, and the engine is simple and compact in structure.
Further, spring friction groove is for setting up in the ring channel of the axle journal excircle that initiative clutch gear formed, spring friction spare is the circular structure of main part and buckles out the enclosed construction of stiff end, the circular structure of main part has the embedding spring friction groove of radial pretightning force, and as shown in the figure, spring friction spare main part is circular and imbed the spring friction inslot, and circular spring forms radial inside power of cramping, forms the friction, and circular less part outwards takes place to warp and forms the stiff end, and this stiff end and circular main part natural transition form holistic enclosed construction, guarantee that frictional force is lasting and the bulk strength is higher.
The utility model also discloses an engine, the engine adopts a clutch for the engine start-up.
The utility model has the advantages that: the clutch device and the engine for starting the engine of the utility model adopt the separable and meshed transmission structure, and avoid the direct action of the recoil caused by the reverse rotation of the engine on the starting transmission system; the lifting angle of the screw pair can be reasonably set, the problem of inflexible return caused by over-small lifting angle is avoided, and return interference is avoided, so that the problem of component damage caused by recoil caused by reverse rotation of an engine is thoroughly solved.
Drawings
The invention is further described with reference to the following figures and examples.
FIG. 1 is a schematic structural diagram of a starting system of the present invention;
FIG. 2 is a schematic structural view of the present invention;
FIG. 3 is a schematic view of a clutch gear shaft structure;
fig. 4 is a schematic view of the structure of the active clutch gear.
Detailed Description
Fig. 1 is a schematic structural view of a starting system of the present invention, fig. 2 is a schematic structural view of the present invention, fig. 3 is a schematic structural view of a clutch gear shaft, and fig. 4 is a schematic structural view of an active clutch gear; as shown in the figure: the clutch device for starting the engine comprises a clutch gear meshing pair arranged on an engine starting transmission chain;
the clutch gear meshing pair comprises a driving clutch gear 17 and a driven clutch gear 12, and the driving clutch gear 17 is arranged on a clutch gear shaft 10 in a transmission fit manner through a screw pair 16; when the clutch gear shaft 10 is started, the driving clutch gear is driven by the screw pair 16 to move axially to be in meshed transmission with the driven clutch gear, and after the starting is finished, the driving clutch gear 17 is driven to return and is separated from the driven clutch gear 12;
the gear pair formed by the driving clutch gear 17 and the driven clutch gear 12 can be located at any position of a transmission chain of a starting transmission system theoretically and can play a role in disconnecting reverse rotation transmission, but in order to reduce impact on components in actual use, the gear pair is located at the rear end of the output of starting power as far as possible and is close to a crankshaft of an engine;
the rotation direction of the screw pair 16 is based on the requirement of meshing to propel the driving clutch gear to move to the driven clutch gear when the clutch gear shaft rotates, and the details are not repeated;
in the structure, when the electric starting is carried out, the starting motor 1 inputs power to the clutch gear shaft 10, the clutch gear shaft drives the driving clutch gear to axially move through the screw pair to be meshed with the driven clutch gear while rotating, so that the starting power is transmitted to the engine crankshaft (the transmission to the engine crankshaft is realized in various modes, and can be realized through gears, direct connection or other intermediate components), and the starting is realized; after the engine is started, the starting motor is stopped, the engine runs power and returns back to drive the driven clutch gear to rotate, so that the driving clutch gear is driven to rotate, the engine returns along the axial direction of the clutch gear shaft under the action of a spiral pair, the transmission chain is disengaged and disconnected, and at the moment, the engine is flamed out and reversely rotated, so that no influence is caused on the starting of a transmission system; of course, if the active clutch gear is provided with an active return, the effect of disengaging the engagement is better.
The helix angle of the helix pair 16 ensures that the helix pair 16 has no self-locking capability, the helix pair is formed by helix fit, and whether the helix fit can be self-locked or not has a direct relation with the helix angle; in the structure, the parameters of the helix angle are controlled, so that the helix pair can not be self-locked, the return of the active clutch gear after the start is finished is facilitated, and the separation is ensured to be more thorough, thereby ensuring that the impact on a starting system including a starting motor is avoided when the engine rotates reversely;
of course, after the screw pair drives the driving clutch gear to reach the meshing position, the screw pair can be structurally set as a head for driving axial movement so as not to form axial driving, the continuous driving of the axial movement is avoided, and a special positioning piece is not required to be arranged.
In this embodiment, the driving clutch gear 17 is provided with a return pre-tightening force, and the return pre-tightening force has a tendency of separating the driving clutch gear 17 from the driven clutch gear 12; the direction of the return pretightening force is towards the direction of separating the two gears, the active clutch gear is returned, the return pretightening force helps the active clutch gear to return by combining the setting of the helix angle, a stable separation structure is formed, the interference generated during the operation is avoided, and the whole starting system is protected from being impacted.
In this embodiment, the driving clutch gear 17 is provided with a friction member, the friction member is used for forming a friction force with the driving clutch gear 17, and the friction member is arranged for forming a friction to the driving clutch gear, so that a certain torque is provided, and the driving clutch gear is not easily followed up when the clutch gear shaft 10 rotates, thereby ensuring smooth clutch; the friction member may be in various forms, such as an elastic friction member, which is fixedly disposed with respect to a fixed member such as a case, and which causes a set rotational resistance to the driving clutch gear.
As shown in the figures, the utility model is used in the electric starting system of the engine, still include through the first-order driven gear 4 and the second grade driving gear 2 of the vice 5 meshing of end face cam, with the first-order driven gear 4 meshing transmission be equipped with first-order driving gear 3, with the second grade driving gear 2 meshing transmission be equipped with start power input gear 9, start power input gear 9 with power input to separation and reunion gear shaft 10, first-order driving gear 4 is used for inputting the start power of starter motor 1; the end face cam pair 5 is of a sawtooth meshing structure, is in transmission meshing in the starting direction and is in inclined plane matching in the opposite starting direction; the existing duplicate gear is changed into a split structure and has the functions of separation and meshing; when the transmission is started normally, the end face cam pair is used for transmission, when the switch is started by mistake, the motor is started to drive the driving clutch gear to be meshed with the driven clutch gear, the engine rotates back, the back transmission rotating speed enables the rotating speed of the second-stage driving gear to exceed the rotating speed of the first-stage driving gear due to the setting of the transmission ratio, and the end face cam pair is matched through an inclined plane to form overrunning, so that the impact caused by the rotating speed of the engine during the mistake starting is avoided; of course, the primary driven gear and/or the secondary driving gear are required to have an axial movement allowance, and the allowance ensures that the inclined plane is matched to not transmit power and has a return pretightening force.
The end face cam pair 5 is formed by matching a sawtooth-shaped end face cam 501 arranged on the end face of a shaft neck 401 formed by the primary driven gear 4 with a sawtooth-shaped end face cam 502 arranged on the end face of a shaft neck 201 formed by the secondary driving gear 2, the meshing pre-tightening force for driving the end face cam pair to mesh with the first driven gear 4 or/and the secondary driving gear 2 can be independently or respectively arranged, but the pre-tightening force is arranged to have axial movement allowance, and is not described again; the structure is simple and compact, and the shaft neck forms a cam meshing pair, so that the stability of axial movement can be ensured.
In this embodiment, the primary driving gear 3 is disposed on the rotor output shaft of the starting motor 1 in a transmission fit manner, and is used for inputting the starting power of the starting motor 1, as shown in the figure, the embodiment is integrally formed; the starting power input gear 9 is arranged on the clutch gear shaft in a transmission fit manner to input starting power to the clutch gear shaft, and is generally arranged in an integrated manner; the end face cam pair 5 and the spiral pair 16 are arranged in series, so that the interruption of the recoil caused by the reverse rotation of the engine is ensured, and the recoil can be overtaken in time after the engine is started by mistake; the isolator in the prior art is eliminated, the cost is saved, and the structure of the engine is simplified.
In this embodiment, the screw pair 16 is formed by matching an inner screw 1602 of the active clutch gear 17 with an outer screw 1601 of the clutch gear shaft 10, and the return pretightening force is applied by a return spring 14 which is externally sleeved on an extending shaft section of the clutch gear shaft and one end of which abuts against the active clutch gear and the other end of which is axially fixed relative to the clutch gear shaft; the end of the return spring 14 is generally fixed axially by a stopper 13 fixed to the clutch gear shaft; as shown in the figure, the clutch driving gear 17 is arranged on the clutch gear shaft 10 close to the starting power input gear 9 through the screw pair 16, the return spring 14 is sleeved at the far end of the clutch gear shaft 10, the driven clutch gear 12 is arranged at the other side of the driving clutch gear 17 relative to the starting power input gear 9, the whole structure is compact, the arrangement is reasonable, and for the driving clutch gear 17, a limiting part for avoiding disengagement does not need to be arranged independently.
The return spring 14 has an elastic coefficient of a set value, is compressed to a position where the two gears are meshed under the set value, is matched with the helix angle, and has an elastic force capable of preventing the driving clutch gear from continuing to move axially, so that starting meshing can be ensured, and a separate limiting part is not required to be arranged.
In this embodiment, the friction member is a spring friction member 15, a spring friction groove is formed in an outer circle of the active clutch gear 17, and the spring friction member 15 has a fixed end 1501 which has a set pre-tightening force embedded in the spring friction groove and extends out of the spring friction groove and is relatively fixed; the spring friction piece adjusts a proper pretightening force for applying a friction force to the active clutch gear, of course, the spring should have a fixed end for supporting the generation of the friction force, and the fixed end can be fixed at a specific position of the engine box body according to the installation requirement, and is not described herein again; the driven clutch gear is directly connected to a magneto rotor in a transmission mode, so that power is transmitted to an engine crankshaft, a one-way clutch is removed, and the structure is simple and compact.
In this embodiment, the primary driven gear 4 and the secondary driving gear 2 are rotationally matched and sleeved on an intermediate shaft 7, and the meshing pretightening force is applied by a meshing spring 8 which is sleeved on the intermediate shaft 7, one end of the meshing pretightening force abuts against the primary driven gear 4, and the other end of the meshing pretightening force is axially fixed relative to the intermediate shaft; as shown in the figure, the first-stage driven gear 4 should also move axially relative to the intermediate shaft 7, one end of the meshing spring 8 abuts against the limiting part 6 fixed on the intermediate shaft 7, and the other end of the meshing spring abuts against the first-stage driven gear 4 and applies a pre-tightening force to enable the first-stage driven gear to move towards the second-stage driving gear 2, so that meshing separation smoothness is guaranteed.
In this embodiment, the spring friction member 15 is a closed structure with a circular main body and a bent fixed end, as shown in the figure, the spring friction groove is an annular groove formed on a shaft neck of the active clutch gear, the main body of the spring friction member 15 is circular and is embedded into the spring friction groove, the circular spring forms radial inward tightening force to form friction, the circular smaller part deforms outwards to form the fixed end 1501, the fixed end and the circular main body naturally transition to form the integral closed structure, and the durability of the friction force and the high integral strength are ensured.
The utility model also discloses an engine, the engine adopts a clutch for the engine start-up, get rid of prior art's isolator, reduce the volume of engine and simplify the assembly process. The utility model is used for in the engine, the jackshaft (fixed or rotation) that uses in clutch gear axle (rotation) and the system all supports in the relevant position of engine box etc. belongs to current mounting structure, no longer gives unnecessary details here.
Finally, although the present invention has been described in detail with reference to the preferred embodiments, it should be understood by those skilled in the art that the present invention can be modified or replaced by other means without departing from the spirit and scope of the present invention, which should be construed as limited only by the appended claims.
Claims (9)
1. A clutch device for engine starting, characterized in that: the clutch gear meshing pair is arranged on an engine starting transmission chain;
the clutch gear meshing pair comprises a driving clutch gear and a driven clutch gear, and the driving clutch gear is arranged on a clutch gear shaft in a transmission fit manner through a spiral pair; when the clutch gear shaft is started, the driving clutch gear is driven by the spiral pair to move axially to be in meshed transmission with the driven clutch gear when the clutch gear shaft rotates, and after the starting is finished, the driving clutch gear is driven to return and is separated from the driven clutch gear.
2. The clutch device for engine start according to claim 1, characterized in that: the driving clutch gear is provided with a return pretightening force, and the return pretightening force has a tendency of separating the driving clutch gear from the driven clutch gear.
3. The clutch device for engine start according to claim 1, characterized in that: the driving clutch gear is provided with a friction piece, and the friction piece is used for forming friction force with the driving clutch gear.
4. The clutch device for engine start according to claim 1, characterized in that: the helix angle of the helical pair makes the helical pair not have self-locking capability.
5. The clutch device for engine start according to claim 2, characterized in that: the spiral pair is formed by matching an inner spiral of the driving clutch gear with an outer spiral of the clutch gear shaft, the return pretightening force is applied by a return spring which is sleeved outside an extending shaft section of the clutch gear shaft and one end of the return pretightening force props against the driving clutch gear, and the other end of the return pretightening force is axially fixed relative to the clutch gear shaft.
6. The clutch device for engine start according to claim 3, characterized in that: the friction piece is a spring friction piece, the excircle of the active clutch gear is provided with a spring friction groove, and the spring friction piece is provided with a fixed end which is embedded in the spring friction groove and relatively fixed when the spring friction piece is stretched out for use.
7. The clutch device for engine start according to claim 2, characterized in that: the clutch gear shaft is provided with a starting power input gear in a transmission fit manner; the driven clutch gear is used for driving and directly connecting to a magneto rotor, so that power is transmitted to an engine crankshaft.
8. The clutched device for engine starting of claim 6, wherein: the spring friction groove is an annular groove formed in the outer circle of a shaft neck formed by the active clutch gear, the spring friction piece is of a main body circular structure and is bent to form a closed structure of a fixed end, and the main body circular structure is provided with an embedded spring friction groove with radial pretightening force.
9. An engine, characterized in that: the engine employs the clutch device for engine starting according to any one of claims 1 to 8.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201920297412 | 2019-03-07 | ||
| CN2019202974124 | 2019-03-07 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN210343568U true CN210343568U (en) | 2020-04-17 |
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ID=70180217
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201920543114.9U Expired - Fee Related CN210343568U (en) | 2019-03-07 | 2019-04-19 | Clutch device for starting engine and engine |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN210343568U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109973276A (en) * | 2019-03-07 | 2019-07-05 | 重庆隆鑫发动机有限公司 | Engine starting system and engine |
| CN113037007A (en) * | 2021-02-22 | 2021-06-25 | 深圳市合涟聚电子科技有限责任公司 | Driving device for starting and generating power for automobile |
| CN113217556A (en) * | 2021-05-31 | 2021-08-06 | 长沙理工大学 | Impact-free gear clutch structure |
-
2019
- 2019-04-19 CN CN201920543114.9U patent/CN210343568U/en not_active Expired - Fee Related
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109973276A (en) * | 2019-03-07 | 2019-07-05 | 重庆隆鑫发动机有限公司 | Engine starting system and engine |
| CN113037007A (en) * | 2021-02-22 | 2021-06-25 | 深圳市合涟聚电子科技有限责任公司 | Driving device for starting and generating power for automobile |
| CN113037007B (en) * | 2021-02-22 | 2022-06-03 | 深圳市合涟聚电子科技有限责任公司 | Driving device for starting and generating power for automobile |
| CN113217556A (en) * | 2021-05-31 | 2021-08-06 | 长沙理工大学 | Impact-free gear clutch structure |
| CN113217556B (en) * | 2021-05-31 | 2022-02-15 | 长沙理工大学 | Impact-free gear clutch structure |
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| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20200417 |
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| CF01 | Termination of patent right due to non-payment of annual fee |