CN204327880U - The two clutch speed-changing differential mechanism of linking type - Google Patents

Abstract

The utility model discloses a linkage type dual-clutch variable speed differential, which comprises a dual clutch and a variable speed differential assembly. The dual clutch includes a first clutch, a second clutch and a clutch control mechanism. The first clutch and the second The two clutches are alternately engaged or disengaged through the control of the clutch control mechanism. The linked dual-clutch variable speed differential of the utility model is low in cost, small in size and light in weight, and can greatly enhance the scope of application of the linked double clutch variable speed differential. It is suitable for small-sized vehicles with strict cost control, such as electric vehicles.

Description

Linkage dual clutch transmission differential

technical field

The utility model relates to the field of motor vehicle parts, in particular to a linkage type dual-clutch variable speed differential.

Background technique

Dual-clutch transmission combines the advantages of manual transmission and automatic transmission. Instead of using a torque converter, it uses two sets of clutches. The two sets of clutches work alternately to achieve the effect of seamless shifting, which not only makes the car The driving becomes easier, and it also effectively improves the comfort, power and safety of the car. The dual clutch is responsible for gear shifting, start control, power transmission, torsional vibration reduction, overload protection and other important functions. It is a key component of the dual clutch transmission system. The two clutch components of the clutch are respectively controlled by two independent electro-hydraulic control systems, thereby respectively controlling the switching of two different gear positions of the dual clutch. This automatic control system has a complex structure and high cost. Therefore, the existing linkage type Dual-clutch variable speed differentials are difficult to apply to vehicles with limited space and low cost space such as electric vehicles.

Therefore, in order to solve the above problems, there is a need for a linkage type dual-clutch speed differential that only needs a set of operating mechanisms to control the two independent clutch assemblies in the dual-clutch, greatly simplifying its structure and low cost.

Utility model content

In view of this, the purpose of this utility model is to overcome the defects in the prior art and provide a linkage type dual-clutch speed differential with simple structure, high transmission efficiency and low cost.

The linkage type dual-clutch variable speed differential of the utility model includes a dual clutch and a variable speed differential assembly. The dual clutch includes a first clutch, a second clutch and a clutch control mechanism. The first clutch and the second clutch pass through The clutch operating mechanism controls alternate engagement or disengagement;

Further, the clutch operating mechanism includes a first pressure plate and a second pressure plate, the first pressure plate and the second pressure plate have linkage cooperation and are used to drive the first clutch and the second clutch to alternately engage or disengage;

Further, both the first clutch and the second clutch are friction disc clutches, and the second pressure plate is provided with a pre-tightening force for engaging the second clutch, and the first pressure plate can overcome the pre-tightening force and form a joint with the second pressure plate. Linkage and disengage the second clutch and engage the first clutch;

Further, the clutch operating mechanism also includes a clutch sleeve arranged in cooperation with the input end of the dual clutch, and the first pressure plate and the second pressure plate are both connected to the clutch sleeve in an axial sliding circumferential direction transmission mode and pre-tightened. The force is set between the clutch sleeve and the first pressure plate or between the clutch sleeve and the second pressure plate;

Further, the second pressure plate is provided with a guide post in the axial direction, and the guide post is fixedly connected to the first pressure plate through the clutch sleeve. The pretightening force includes setting between the clutch sleeve and the first pressure plate or the clutch core Spring I between the sleeve and the second pressure plate;

Further, the second pressure plate is provided with a guide post along the axial direction, the guide post passes through the clutch sleeve and the second pressure plate and is fixedly connected to a push plate, and the pre-tightening force includes setting between the first pressure plate and the push plate. The spring I between and the spring II arranged between the first pressure plate and the clutch sleeve;

Further, the guide post is provided with a limit step for axially limiting the first pressure plate, and the elastic coefficient of spring I is greater than that of spring II;

Further, the first clutch includes a first moving friction plate fixed on the clutch sleeve and a first static friction plate matched with the first moving friction plate, and the second clutch includes a second moving friction plate fixed on the clutch sleeve and a first static friction plate matched with the second moving friction plate. The second static friction plate matched with the plate; the first clutch also includes a first clutch housing fixedly connected with the first static friction plate, the second clutch also includes a second clutch housing fixedly connected with the second static friction plate, the first clutch housing coaxially arranged with the second clutch housing and the first clutch housing is accommodated in the second clutch housing;

Further, the variable speed differential assembly also includes a transmission and a differential, the transmission includes an input shaft and an output shaft, the input shaft is rotatably provided with a driving gear I and a driving gear II, and the output shaft is driven and provided with a driven gear Gear I and driven gear II, the input shaft is in transmission connection with the input end of the clutch, and the driving gear I and driving gear II are in transmission connection with the first clutch housing and the second clutch housing respectively;

Further, the differential includes a differential case and a differential gear assembly, and the differential case is drive-cooperated with a differential gear configured to drive-cooperate with the output shaft.

The beneficial effects of the utility model are: in the linkage type dual-clutch transmission differential of the utility model, the clutch control mechanism controls the first clutch and the second clutch to alternately engage or separate, therefore, the control of the dual-clutch can adopt an automatic clutch with a simple structure. The control system can even realize manual control. Therefore, the linkage type dual-clutch variable speed differential of the utility model has low cost, small size and light weight, which can greatly enhance the scope of application of the dual-clutch, making it suitable for loading on electric vehicles and other small , Vehicles with strict cost control.

Description of drawings

Below in conjunction with accompanying drawing and embodiment the utility model is further described:

Fig. 1 is the structural representation of the utility model.

Detailed ways

Fig. 1 is a structural schematic diagram of the present utility model, as shown in the figure, the linked dual-clutch transmission differential of the present embodiment includes a dual clutch and a transmission differential assembly, and the dual clutch includes a first clutch, a second clutch and a clutch The operating mechanism, the first clutch and the second clutch are alternately engaged or disengaged through the clutch operating mechanism. Therefore, the control of the linkage type dual-clutch transmission differential can adopt an automatic control system with a simple structure, or even manual control. The dual clutch of this embodiment has low cost, small size and light weight, which can greatly enhance the scope of application of the dual clutch, making it suitable for being mounted on electric vehicles and other small vehicles with strict cost control;

In this embodiment, the clutch operating mechanism includes a first pressure plate 13 and a second pressure plate 7, and the first pressure plate 13 and the second pressure plate 7 have linkage cooperation and are used to drive the first clutch and the second clutch alternately. Engagement or disengagement, the first clutch and the second clutch can adopt all existing clutch structures, such as friction plate clutches, jaw clutches, etc., and make the first clutch correspondingly through the first pressure plate 13 and the second pressure plate 7 Engaged or separated from the second clutch, the first pressure plate 13 and the second pressure plate 7 can be fixedly connected or elastically connected to form a linkage cooperation, and then when the first pressure plate 13 is pressed, the second pressure plate 7 Disengagement; similarly, when the second pressure plate 7 is pressed, the first pressure plate 13 is separated, so that the first clutch and the second clutch are alternately engaged or disengaged.

In this embodiment, both the first clutch and the second clutch are friction disc clutches, the second pressure plate 7 is provided with a pre-tightening force for engaging the second clutch, and the first pressure plate 13 can overcome the pre-tightening force and The second pressure plate 7 forms a linkage to separate the second clutch and engage the first clutch. The engagement and separation of the friction plate clutch is realized by pressing or loosening the friction plate. The pre-tightening force can be realized by elastic elements such as springs , so that the second clutch is always engaged, the first clutch is always disengaged, and when the first pressure plate 13 is pushed, the first pressure plate 13 can overcome the pre-tightening force and press the first clutch. At the same time, because the first pressure plate 13 There is a linkage cooperation with the second pressure plate 7, the second pressure plate 7 will be separated, and finally the first clutch will be engaged and the first clutch will be disengaged.

In this embodiment, the clutch control mechanism also includes a clutch core sleeve 5 arranged in cooperation with the input end of the double clutch, and the first pressure plate 13 and the second pressure plate 7 are connected to the clutch in the manner of axial sliding and circumferential transmission. The core sleeve 5 is connected and the pretightening force is set between the clutch core sleeve 5 and the first pressure plate 13 or between the clutch core sleeve 5 and the second pressure plate 7; the outer cylindrical surface of the clutch core sleeve 5 is provided with a spacer ring 10 along the circumferential direction, The first pressure plate 13 and the second pressure plate 7 are arranged on both sides of the spacer ring 10 along the axial direction, the first clutch is located between the spacer ring 10 and the first pressure plate 13, and the second clutch is located between the spacer ring 10 and the second pressure plate. Between the discs 7, since the clutch core sleeve 5 is in transmission connection with the first pressure plate 13 and the second pressure plate 7, the first pressure plate 13 and the second pressure plate 7 will follow the clutch core sleeve 5, and the elastic force can be compressed. The spring or tension spring makes the second pressure plate 7 always press against the spacer ring 10 without external force so that the second clutch is always engaged.

In this embodiment, the second pressure plate 7 is provided with guide pillars 16 along the axial direction, and a plurality of guide pillars 16 can be evenly distributed along the circumferential direction of the first pressure plate 13, and the clutch core sleeve 5 is correspondingly provided with through holes to guide The column 16 passes through the clutch core sleeve 5 and is fixedly connected to the first pressure plate 13 (the matching form of the first pressure plate 13 and the second pressure plate 7 is not shown in the drawings), and the pretightening force includes The spring I17 between the sleeve 5 and the first pressure plate 13 or between the clutch core sleeve 5 and the second pressure plate 7, if the spring I17 adopts a compression spring, the spring I17 should be set between the clutch core sleeve 5 and the first pressure plate 13 In between, if the spring I17 is a tension spring, the spring I17 should be arranged between the clutch sleeve 5 and the second pressure plate 7 .

In this embodiment, the following cooperation form can also be adopted between the first pressure plate 13, the second pressure plate 7 and the clutch sleeve 5: the second pressure plate 7 is provided with a guide post 16 along the axial direction, and the guide post 16 is arranged along the first There are multiple pressure plates 13 evenly distributed in the circumferential direction. The guide post 16 passes through the clutch sleeve 5 and the second pressure plate 7 and is fixedly connected to a push plate 14. The spring I17 between the first pressure plate 13 and the spring II19 arranged between the first pressure plate 13 and the clutch sleeve 5, where the spring I17 and the spring II19 are both compression springs, when the push plate 14 is not affected by external force, the push plate 14 Under the joint action of spring I17 and spring II19, it will move away from the clutch sleeve 5, and then drive the second pressure plate 7 to press the spacer ring 10 to make the second clutch normally engaged; The effect will also be far away from the spacer ring 10, so that the first clutch is often separated; when the push plate 14 is subjected to external force to make it move to the side of the clutch sleeve 5, the second pressure plate 7 will move away from the spacer ring 10, so that the second clutch Separate; and the spring II19 is compressed to make the first pressure plate 13 overcome the elastic force of the spring I17 and press to the side of the spacer ring 10, the first clutch will be engaged. In this embodiment, the center of the push plate 14 is rotatably connected with a push pin 15, By manipulating the push pin 15 to move in the axial direction, the push plate 14 can be pushed to reciprocate in the axial direction, thereby controlling the separation and engagement of the first clutch and the second clutch.

In this embodiment, the guide post 16 is provided with a limit step 18 for axially limiting the first pressure plate 13, the elastic coefficient of the spring I17 is greater than that of the spring II19, and the limit step 18 can ensure When the second clutch is engaged, the second pressure plate 7 is far away from the spacer ring 10, ensuring that the second clutch is disengaged while the first clutch is engaged; When pushing toward the clutch sleeve 5, ensure that the pressure of the spring I17 on the first pressure plate 13 can quickly overcome the elastic force of the spring II19 to make the first pressure plate 13 press the first clutch and engage it.

In this embodiment, the first clutch includes a first moving friction plate 11 fixed on the clutch sleeve 5 and a first static friction plate 12 matched with the first moving friction plate 11, and the second clutch includes a first moving friction plate 12 fixed on the clutch sleeve 5. The second dynamic friction plate 8 and the second static friction plate 9 matched with the second dynamic friction plate 8, the first pressure plate 13 can move in the axial direction and then compress the first dynamic friction plate 11 and the first static friction plate 12 and make them engage, because the second A moving friction plate 11 is fixed on the clutch sleeve 5, and the clutch sleeve 5 is in transmission connection with the input end of the clutch. Therefore, after the first pressure plate 13 is compressed, the power can be transmitted from the input end to the first static friction plate 12, and finally output The same is true for the second pressure plate 7. Again, the first clutch also includes a first clutch housing 6 that is fixedly connected to the first static friction plate 12, and the second clutch also includes a first clutch housing 6 that is fixedly connected to the second static friction plate 9. The second clutch housing 4, the first clutch housing 6 is coaxially arranged with the second clutch housing 4 and the first clutch housing 6 is contained in the second clutch housing 4, when the first clutch is engaged, the first clutch housing 6 will be connected with the second clutch housing 4 The clutch core sleeve 5 rotates synchronously, and the first clutch housing 6 can be connected with the output terminal to drive and output torque. Similarly, after the second clutch is engaged, the torque can also be output through the second clutch housing 4, which will not be repeated again. A clutch housing 6 is arranged coaxially with the second clutch housing 4 and the first clutch housing 6 is accommodated in the second clutch housing 4. This arrangement can significantly improve the compactness of the double clutch structure.

In this embodiment, the transmission differential assembly also includes a transmission and a differential, the transmission includes an input shaft 1 and an output shaft 22, the input shaft 1 is rotatably provided with a driving gear I3 and a driving gear II2, and the output shaft 22. Driven gear I20 and driven gear II21 are provided for transmission coordination. The input shaft 1 is in transmission connection with the input end of the clutch. The driving gear I3 and driving gear II2 are respectively in transmission connection with the first clutch housing 6 and the second clutch housing 4. When When the first clutch is engaged, the driving gear I3 is connected to the input shaft 1. At this time, the input shaft 1 and the output shaft 22 are engaged with each other through the driving gear I3 and the driven gear I20. When the second clutch is engaged, the The driving gear II2 is in drive connection with the input shaft 1. At this time, the input shaft 1 and the output shaft 22 are driven through the meshing transmission of the driving gear II2 and the driven gear II21, thereby realizing gear shifting.

In this embodiment, the differential includes a differential housing 24 and a differential gear assembly, and the differential gear 23, which is configured to drive and cooperate with the output shaft, finally passes through the differential. The sun gear 25 in the gear assembly outputs the power to the half shafts.

Finally, it is noted that the above embodiments are only used to illustrate the technical solutions of the present utility model without limitation. Although the utility model has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the utility model can be Modifications or equivalent replacements of the technical solutions without departing from the purpose and scope of the technical solutions of the utility model shall be covered by the claims of the utility model.

Claims (10)

1. the two clutch speed-changing differential mechanism of linking type, it is characterized in that: comprise double clutch and Transaxle assembly, described double clutch comprises first clutch, second clutch and clutch operation, and described first clutch controls alternately to engage or be separated by this clutch operation with second clutch.

2. the two clutch speed-changing differential mechanism of linking type according to claim 1, it is characterized in that: described clutch operation comprises the first platen and the second platen having between described first platen and the second platen and be linked and engage for driving first clutch and second clutch to replace or be separated.

3. the two clutch speed-changing differential mechanism of linking type according to claim 2, it is characterized in that: described first clutch and second clutch are friction plate clutch, second platen is provided with the pretightening force that second clutch is engaged, and the first platen can overcome this pretightening force and be formed with the second platen and link and second clutch be separated and first clutch is engaged.

4. the two clutch speed-changing differential mechanism of linking type according to claim 3, it is characterized in that: described clutch operation also comprises the clutch heart cover be equipped with the input end transmission of double clutch, described first platen and the second platen all overlap with the mode of the circumferencial direction transmission that slides axially and the clutch heart and to be connected and described pretightening force is arranged at the clutch heart overlaps between the first platen or the clutch heart overlaps between the second platen.

5. the two clutch speed-changing differential mechanism of linking type according to claim 4, it is characterized in that: described second platen is provided with guide pillar vertically, described guide pillar is fixedly connected with the first platen through clutch heart cover, and described pretightening force comprises and is arranged at the clutch heart and overlaps between the first platen or the clutch heart overlaps spring I between the second platen.

6. the two clutch speed-changing differential mechanism of linking type according to claim 4, is characterized in that: described second platen is provided with guide pillar vertically, and described guide pillar overlaps with the second platen through the clutch heart and is fixedly connected on a push-plate; Described pretightening force comprise the spring I that is arranged between the first platen and push-plate and be arranged at the first platen and the clutch heart overlap between spring II.

7. the two clutch speed-changing differential mechanism of linking type according to claim 6, it is characterized in that: described guide pillar is provided with the limited step for carrying out axial limiting to the first platen, the elasticity coefficient of described spring I is greater than the elasticity coefficient of spring II.

8. the two clutch speed-changing differential mechanism of linking type according to claim 4, is characterized in that: described first clutch comprises the first movable friction plate being fixed on clutch heart cover and the first static friction sheet coordinated with the first movable friction plate; Described second clutch comprises the second movable friction plate being fixed on clutch heart cover and the second static friction sheet coordinated with the second movable friction plate; Described first clutch also comprises the first clutch shell be fixedly connected with the first static friction sheet; Described second clutch also comprises the second clutch shell be fixedly connected with the second static friction sheet; Described first clutch shell and second clutch shell are coaxially arranged and first clutch shell is contained within second clutch shell.

9. the two clutch speed-changing differential mechanism of linking type according to claim 8, it is characterized in that: described Transaxle assembly also comprises speed changer and differential mechanism, described speed changer comprises input shaft and output shaft, described input shaft is rotatably equipped with driving gear I and driving gear II, and described output shaft transmission is equipped with driven gear I and driven gear II; The input end of described input shaft and double clutch is in transmission connection; Described driving gear I and driving gear II are in transmission connection with first clutch shell and second clutch shell respectively.

10. the two clutch speed-changing differential mechanism of linking type according to claim 9, is characterized in that: described differential mechanism comprises differential casing and differential gear assembly and differential casing transmission is equipped with differential gear for coordinating with output shaft transmission.