KR102465412B1 - Automatic shift engaging 2-speed transmission for a light vehicle - Google Patents

Abstract

The present invention relates to a two-speed transmission device for a compact vehicle capable of automatic shift control. The two-speed transmission device for the compact vehicle capable of automatic shift control of the present invention comprises: one Ravenue planetary gear set; one reduction gear; a clutch; a loading cam; and a one-way clutch. Therefore, two-speed shift is automatically realized by an operation of the loading cam and the clutch according to a speed.

Description

A two-speed transmission mechanism for a compact vehicle capable of automatic transmission control {AUTOMATIC SHIFT ENGAGING 2-SPEED TRANSMISSION FOR A LIGHT VEHICLE}

The present invention relates to a two-speed transmission mechanism for a compact vehicle capable of automatic transmission control, and more particularly, according to the speed, It relates to a two-speed transmission mechanism for an ultra-compact vehicle capable of automatic shift control that automatically implements two-speed shifting.

In general, an electric vehicle refers to an eco-friendly vehicle that does not emit exhaust gas because electricity is used as a power source, unlike a gasoline vehicle using gasoline or a diesel vehicle using diesel. Recently, many advanced car makers, including China, are making great efforts to develop such electric vehicles.

The electric vehicle power source consists of a high-voltage battery, and uses secondary batteries such as nickel-cadmium, nickel-hydrogen, and lithium-ion batteries that can be recharged and have a large capacity.

Since the driving motor, which is the power source of the electric vehicle, is rotationally driven by the electric energy of the high-voltage battery, the rotational force and rotational speed of the driving motor may be directly controlled through the vehicle control unit and thus the vehicle speed may be changed accordingly. That is, since the electric vehicle can easily control the driving motor unlike the internal combustion engine vehicle, the vehicle speed can be smoothly changed through the control of the driving motor without a separate transmission device.

On the other hand, when the vehicle speed is controlled through the control of the driving motor, a large load is applied to the driving motor, the electric energy consumption increases, and accordingly, the mileage through one charge is shortened. There was a problem in that the configuration of the driving motor was complicated and the capacity was increased.

As the vehicle speed increases, the speed of the driving motor must also increase accordingly, high torque is required at low speed, and low torque is required at high speed. The research and development of the existing gasoline vehicle or diesel vehicle is being used by improving the automatic or manual transmission.

Such an automatic transmission or a manual transmission has a disadvantage in that the size of the device is large or the shifting is complicated by using a relatively bulky hydraulic wet multi-plate clutch or by using a synchronizer with high possibility of wear and noise.

Republic of Korea Patent Publication No. 10-1282691 (Title of the invention: 2-speed transmission for electric vehicles, 2013. 07. 05. Announcement)

An object of the present invention is to solve the problems of the prior art, by the operation of the loading cam and clutch according to the speed, including one lavigne planetary gear set, one reduction gear, a clutch, a loading cam, and a one-way clutch. An object of the present invention is to provide a two-speed transmission mechanism for an ultra-compact vehicle capable of automatic shift control that automatically implements two-speed shifting.

The problems of the present invention are not limited to the problems mentioned above, and other problems not mentioned will be clearly understood by those skilled in the art from the following description.

In order to solve the above problems, the two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to the present invention includes an input shaft through which power is introduced from a power source, a reduction gear connected to the input shaft, and a lavigne planet connected to the reduction gear. a gear set, a loading camshaft branched from the input shaft, a loading cam connected to one side of the loading camshaft, and a clutch connected to the other side and one side of the loading cam, wherein the other side and the output shaft of the clutch are connected to the lavigne planet It is connected to the gear set, and the clutch is engaged and released by the operation of the loading cam according to the rotation speed of the input shaft.

Here, the lavigne planetary gear set includes a first sun gear, a second sun gear, a carrier, and a ring gear, wherein the first sun gear is connected to the reduction gear and the ring gear is connected to the other side of the clutch, The carrier further includes a first one-way clutch connected to the output shaft and connected to the ring gear.

In addition, the two-speed transmission mechanism for an ultra-small vehicle capable of automatic transmission control according to the present invention further includes a counter gear connected to the reduction gear, and the lavigne planetary gear set includes a first sun gear, a second sun gear, a carrier and a ring gear. wherein the first sun gear is connected to the counter gear, the second sun gear is connected to the other side of the clutch, the carrier is connected to the output shaft, one side is connected to the first sun gear, and the other side is connected to the It further includes a second one-way clutch connected to the second sun gear.

In addition, the loading cam of the two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to the present invention includes a first cam flange connected to the loading camshaft, a second cam flange connected to one side of the clutch, and the first cam a cam roller interposed between a flange and the second cam flange, wherein the first cam flange and the second cam flange are formed such that the cam roller moves outward as the rotational speed of the loading camshaft increases do.

According to the two-speed transmission mechanism for a compact vehicle capable of automatic transmission control of the present invention, there are one or more of the following effects.

First, the two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to the present invention does not require a separate actuator during shifting, so the configuration is simple, and the volume is small and the unit cost is low.

Second, there is an effect of improving the efficiency of the vehicle because there is no need for a complicated control device, so there is no trouble, and unnecessary power is not used because the speed is automatically changed according to the rotational speed by the loading cam.

Third, it is possible to create a clutch engagement and release gap adjustment profile by optimizing the angle of the swash plate of the loading cam, thereby minimizing shift shock and improving the quality of the transmission mechanism.

The effects of the present invention are not limited to the effects mentioned above, and other effects not mentioned will be clearly understood by those skilled in the art from the description of the claims.

1 is a view showing the overall configuration of a two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to an embodiment of the present invention.
2 is a configuration of a Lavinyu planetary gear set of a two-speed transmission mechanism for an ultra-small vehicle capable of automatic transmission control according to an embodiment of the present invention (FIG. 2 (a)) and a configuration of a loading cam (FIG. 2 (b)) is a diagram showing
3 is a view showing a detailed configuration of a two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to a first embodiment of the present invention.
4 is a view showing a detailed configuration of a two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to a second embodiment of the present invention.
5 is a view showing the configuration of a two-speed transmission mechanism for a micro-vehicle capable of automatic transmission control in the second embodiment of the present invention during first-speed driving.
6 is a view showing the configuration of a two-speed transmission mechanism for an ultra-small vehicle capable of automatic transmission control in a second embodiment of the present invention during two-speed driving.

Advantages and features of the present invention and methods of achieving them will become apparent with reference to the embodiments described below in detail in conjunction with the accompanying drawings. However, the present invention is not limited to the embodiments disclosed below, but may be implemented in various different forms, and only these embodiments allow the disclosure of the present invention to be complete, and common knowledge in the technical field to which the present invention pertains It is provided to fully inform those who have the scope of the invention, and the present invention is only defined by the scope of the claims. Like reference numerals refer to like elements throughout.

The size or shape of the components shown in the drawings attached to this specification may be exaggerated for clarity and convenience of explanation. It should be noted that the same configuration in each drawing is sometimes illustrated with the same reference numerals. In addition, detailed descriptions of functions and configurations of known technologies that may unnecessarily obscure the gist of the present invention may be omitted.

The terminology used herein is used to describe specific embodiments, not to limit the present invention. As used herein, the singular form may include the plural form unless the context clearly dictates otherwise. In addition, when a part "includes" a certain component throughout the present specification, it means that other components may be further included unless otherwise stated.

When a component is referred to as being “connected” or “connected” to another component, it may be directly connected or connected to the other component, but it is understood that other components may exist in between. it should be On the other hand, when it is said that a certain element is "directly connected" or "directly connected" to another element, it should be understood that no other element is present in the middle. Other expressions for describing the relationship between components should be interpreted similarly.

As used herein, terms such as upper, lower, upper, lower or upper, lower, etc. are used to distinguish relative positions of the components. For example, for convenience, when naming the upper part of the drawing as the upper part and the lower part of the drawing as the lower part, the upper part may be called the lower part and the lower part may be called the upper part without departing from the scope of the present invention. .

Terms including ordinal numbers such as ~1~, ~2~, etc. described in this specification may be used to describe various components, but the components are not limited by the terms. The above terms are only used to distinguish each component from each other, and are not limited to the order of manufacture, and the names may not match in the detailed description of the invention and the claims.

All terms including technical or scientific terms used herein have the same meaning as commonly understood by those of ordinary skill in the art to which the present invention belongs, unless otherwise defined. Terms such as those defined in commonly used dictionaries should be interpreted as having a meaning consistent with the meaning in the context of the related art, and should not be interpreted in an ideal or excessively formal meaning unless explicitly defined in the present specification. does not

Hereinafter, the present invention will be described with reference to the drawings in order to describe a two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to embodiments of the present invention.

1 is a view showing the overall configuration of a two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to an embodiment of the present invention.

Referring to FIG. 1 , a two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to an embodiment of the present invention includes an input shaft 100 to which power is introduced from a power source, a reduction gear 200 connected to the input shaft, and the reduction gear Lavinue planetary gear set 300 connected to, a loading camshaft 400 branched from the input shaft 100, a loading cam 500 having one side connected to the loading camshaft 400, and the loading cam 500 It includes a clutch 600 to which the other side and one side are connected, but the other side and the output shaft 700 of the clutch 600 are connected to the lavigne planetary gear set 300, and according to the rotation speed of the input shaft 100 It is characterized in that the clutch (600) is engaged and released by the operation of the loading cam (500).

The power output from the power source is transmitted to the reduction gear 200 by the input shaft 100 , is decelerated at a constant speed in the reduction gear 200 , and is input to the LAVINUE planetary gear set 300 .

Here, the Lavinue planetary gear set 300 will be described in detail with reference to FIG. 2A as follows.

Lavinue planetary gear set 300 is basically two sun gears (first sun gear, second sun gear) having different diameters, a pinion (first pinion, second pinion) connected to them, and a central shaft of two pinions and It consists of a carrier which is connected to form a single rotating body and a ring gear connected to the carrier. In the Lavinue planetary gear set 300 , two sun gears, a carrier, and a ring gear may be input and output, respectively, and the rest may be fixed, freely rotated, or connected to each other to rotate together. For example, the first sun gear, which is a component of the Lavinue planetary gear set, may have a configuration such as the first input, the second sun gear as the second input, the carrier as the output, and the ring gear as coupling/disengaging to the transmission housing as a clutch. have.

In the case of the Lavinue planetary gear set 300, referring to FIG. 2 (a), the speed expression according to the gear ratio can be obtained as follows.

(1-Rss)Wc = Wr - RssWss (Equation 1)

(1+Rls)Wc = Wr + RlsWls (Equation 2)

(1-Rlp)Wc = Wr - RlpWlp (Equation 3)

(1+Rsp)Wc = Wr + RspWsp (Equation 4)

Here, R (in FIG. 2 (a), r means a radius) means a gear ratio, and Rss means a gear ratio of the ring gear to a first small sun gear gear ratio, that is, Zss/Zr. (Zr is the number of gears of the ring gear, Zss is the number of gears of the first sun gear, and in FIG.

Similarly, Rls is the gear ratio of the large sun gear to the gear ratio of the ring gear, Rsp is the gear ratio of the first pinion to the gear ratio of the ring gear, and Rlp is the gear ratio of the ring gear to the second pinion (large pinion). ) means the gear ratio.

In addition, Wc is the rotational speed of the carrier, Wss is the rotational speed of the first small sun gear, Wls is the rotational speed of the second large pinion, Wsp is the rotational speed of the first small pinion, Wlp is the rotational speed of the second pinion, and Wr is the rotational speed of the ring gear.

The two-speed transmission mechanism for a miniature vehicle capable of automatic transmission control according to an embodiment of the present invention is an input of the lavigne planetary gear set 300, and the input from the power source is the input shaft 100 and the loading cam 500 and the clutch 600 ), and the output goes out through the output shaft 700 .

As described above, the input may be any two of the first sun gear, the second sun gear, the carrier, and the ring gear of the Lavinue planetary gear set 300 , and the output may be any one of the others, and the related speed formula is It is determined from Equations 1 to 4.

Hereinafter, operations of the clutch 500 and the loading cam 600 will be described.

As described above, the power output from the power source is input through the reduction gear 200 after passing through the input shaft 100 (first input), and is branched in the middle through the loading camshaft 400 and the loading cam 500 ) is also entered.

Power input to the loading cam 500 is transmitted to the clutch 600 via the loading cam 500, and depending on the state of the loading cam 500, the coupling and disengagement of the clutch 600 are determined, so that the power is The second input is made to the new planetary gear set 300 .

The loading cam 500 includes a first cam flange 510 connected to the loading camshaft 400 , a second cam flange 520 and the first cam flange 510 connected to one side of the clutch 500 . and a cam roller 530 interposed between the second cam flange 520 .

The first cam flange 510 and the second cam flange 520 are formed so that the cam roller 520 moves outward as the rotation speed of the loading camshaft 400 increases.

That is, when the rotational speed of the loading camshaft 400, that is, the rotational speed of the input shaft 100 is lower than a predetermined standard, the cam roller 530 is located at the center of the first cam flange 510 and the second cam flange 520. position, and at this time, the relative distance of the second cam flange 520 compared to the first cam flange 510 becomes close according to the shapes of the first cam flange 510 and the second cam flange 520 .

When the rotational speed of the loading camshaft 400 is higher than a predetermined standard, the cam roller 530 moves outward by centrifugal force, and as it moves outward, the second cam flange 520 compared to the first cam flange 510. The relative distance between the s is increased to drive the clutch 600 . That is, the driving unit of the clutch 600 is pressed and the clutch 600 is coupled.

When the speed of the input shaft 100 reaches a certain standard (constant speed) by the operation of the loading cam 400 , the clutch 600 operates and power is transferred to the lavigne planetary gear set 300 as a second input. will be input

That is, before a certain standard (constant speed), the transmission mechanism operates in 1st gear, and when it exceeds a certain reference (constant speed), the transmission mechanism operates in 2nd gear.

One input comes in from the Lavinue planetary gear set 300 , and the input is changed to two by the operation of the clutch, and accordingly, the gear ratio of the Lavinue planetary gear set 300 is changed.

Various embodiments of such an operation may exist, and the present invention will be described in detail through two embodiments.

3 is a view showing a detailed configuration of a two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to a first embodiment of the present invention.

Referring to FIG. 3 , the power coming through the input shaft 100 enters the first sun gear 310 of the Lavinue planetary gear set 300 through the reduction gear 200 .

Meanwhile, the other side of the clutch 600 is connected to the ring gear 340 of the Lavinue planetary gear set 300 , and the output shaft 700 is connected to the carrier 330 .

In addition, the ring gear 340 is further connected to the transmission housing (not shown) by the first one-way clutch 800 .

In this configuration, in the case of the first stage, since the rotational speed of the loading cam 500 does not reach a certain standard, the clutch 600 is released, and the first one-way clutch 800 connected to the ring gear 340 is It is locked to the transmission housing and does not rotate.

In the second stage, the rotation speed of the loading cam 500 reaches a predetermined standard, and the clutch 600 is pressed and coupled. That is, the second input is transmitted to the ring gear 340 through the clutch 600 , and at this time, the first one-way clutch 800 is disengaged from the transmission housing due to the rotation direction and can rotate freely.

When the gear ratio of the reduction gear 200 is expressed as N (N is a value less than 1 when deceleration is performed by the number of output gears compared to the number of input gears), the speed equation can be obtained as follows.

In the first stage, since the clutch 600 is released and the first one-way clutch 800 is engaged, Wr = 0, and the above-mentioned Equation 1 becomes as follows.

(1-Rss)Wc = -RssWss (Equation 5)

Here, when the rotational speed of the power source is expressed as Wm, it is transmitted to Wss through the reduction gear 200, so the speed equation is as follows.

Wss = -NWm (Equation 6)

Since the reduction gear 200 changes the rotation speed in the opposite direction, it becomes negative (-), and when Equations 5 and 6 are combined, it becomes as follows.

(1-Rss)Wc = NRssWm (Equation 7)

Here, assuming that Rss = 0.2 and N = 0.8, Wc becomes 0.2 Wm, and thus the operation is decelerated.

In the second stage, as the rotational speed Wm of the power source increases, the loading cam 500 operates to engage the clutch 600 so that Wm and Wr become equal. At this time, the first one-way clutch 800 is released (freewheel, free rotation).

In this case, Equation 1 is changed as follows.

(1-Rss)Wc = Wm + NRssWm (Equation 8)

As above, when Rss = 0.2, N = 0.8, Wc = (0.8/1.16)Wm and Wc = 0.69Wm, which results in a higher rotational speed than the first stage.

On the other hand, in this configuration, the second sun gear 320 rotates freely, and the rotation speed is determined according to the above speed equation. In addition, the speed of the first pinion and the second pinion is determined according to the above-described formula (speed formula).

4 is a view showing a detailed configuration of a two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to a second embodiment of the present invention.

A two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to a second embodiment of the present invention has the following configuration. The first sun gear 310 of the Raviu planetary gear set 300 is connected to the reduction gear 200, the second sun gear 320 is connected to the other side of the clutch 600, and the carrier 330 is the It is connected to the output shaft 700, and the ring gear 340 rotates freely. Here, in the two-speed transmission mechanism for a micro vehicle capable of automatic transmission control according to the second embodiment, one side is connected to the first sun gear 310 and The other side further includes a second one-way clutch 350 connected to the second sun gear 320 .

In this second embodiment, when the reduction gear 200 further includes a counter gear 210 and power is input to the first sun gear 310 through the reduction gear 200 , the rotational direction becomes the same.

5 is a view showing the configuration of a two-speed transmission mechanism for a micro-vehicle capable of automatic transmission control in the second embodiment of the present invention during first-speed driving.

Referring to FIG. 5 , in the first stage, the rotation speed Wm of the power source is not fast, so the loading cam 500 rotates at a low speed, and accordingly, the clutch 600 is not engaged. At this time, the first one-way clutch 350 coupled between the first sun gear 310 and the second sun gear 320 is operated so that the first sun gear 310 and the second sun gear 320 rotate integrally. do. That is, the first one-way clutch 350 is locked in the rotational direction of the first sun gear 310 so that the second sun gear 320 is coupled together to rotate. Since no components are connected to the ring gear 340 and thus freely rotate, the power transmitted while the first sun gear 310 and the second sun gear 320 rotate integrally goes out to the carrier 330 .

Subtracting Equation 1 from Equation 2 above,

(Rls + Rss)Wc = RlsWls + RssWss (Equation 9)

Here, since Wss = Wls, eventually Wss = Wls = Wc, and they all rotate at the same speed.

6 is a view showing the configuration of a two-speed transmission mechanism for an ultra-small vehicle capable of automatic transmission control in a second embodiment of the present invention during two-speed driving.

Referring to FIG. 6 , before describing the second-speed driving, the shifting process from the first gear to the second gear will be described as follows.

When the rotational speed Wm of the power source increases and reaches a certain standard (constant speed), the clutch 600 starts to engage by the axial force applied from the loading cam 500, and the first sun gear 310 and the second The speed of the sun gear 320 is changed. The speed of the first sun gear 310 is relatively slow because the reduction gear 200 is connected, so that the second one-way clutch 350 is released (freewheel, free rotation). .

When the two-speed driving is described with reference to FIG. 6 , since the clutch 600 is engaged and the one-way clutch 350 is released, power from the power source is applied to both the first sun gear 310 and the second sun gear 320 . is entered through Since the ring gear 330 still rotates freely, the rotation speed is determined as shown in Equation 9, and the rotation speed of the carrier 330 is determined by the rotation speed and the gear ratio of the first sun gear 310 and the second sun gear 320 . do.

With reference to the drawings shown in FIGS. 5 and 6 and the above-described equations, the speed at the first and second stages is calculated as follows.

In the first stage, since the rotational speed Wm of the power source is transmitted to the first sun gear 310 through the counter gear 210 via the reduction gear 200, when the reduction gear ratio of the reduction gear 200 is N, Wss = Wls = NWm. That is, the rotation speed of the first sun gear 310 and the second sun gear 320 is the same, and the rotation speed is reduced by the reduction ratio from the power source.

As described above, since the rotation speed of the carrier 330 is the same as the rotation speed of the first sun gear 310 and the second sun gear 320 , the output shaft speed is Wc = Wss = Wls = NWm. For example, when the reduction ratio is 0.5, N = 0.5, and the output shaft speed of the first stage is 0.5 Wm.

In the case of the second stage, the rotation speed of Wc is determined by Equation 9 above. For example, when Rss = 0.2 and Rls = 0.4 (N=0.5 is the same), the speed of the first stage is increased as shown below.

Wc = (RssWss + RlsWls) / (Rss + Rls) (Equation 10)

Wc = (0.2NWm + 0.4Wm) / (0.2 + 0.4) = (0.1Wm + 0.4Wm)/0.6 = 5/6Wm = 0.83Wm

That is, the two-speed transmission mechanism for a compact vehicle capable of automatic transmission control according to the present invention is such that the profile of the cam flange (first, second) of the loading cam is set to a certain standard (constant speed) according to the rotational speed of the power source so that the clutch is coupled. When set, the shift is automatically performed without any special mechanism, and if the gear ratio of the Lavinyu planetary gear set and the gear ratio of the reduction gear are appropriately adjusted, it can be matched to the power source to configure the optimal two-speed transmission.

As described above, preferred embodiments of the present invention have been illustrated and described with reference to the drawings, but the present invention is not limited to the specific embodiments described above, and the present invention is not limited to the specific embodiments described in the claims. Various modifications may be made by those of ordinary skill in the art to which the invention pertains, and these modifications should not be individually understood from the technical spirit or prospect of the present invention.

100: input axis
200: reduction gear
300: Lavinyu Planetary Gear Set
400: loading camshaft
500: loading cam
600: clutch
700: output shaft
800: first one-way clutch
210: counter gear
310: first sun gear
320: second sun gear
330: carrier
340: ring gear
350: second one-way clutch

Claims (3)

In a two-speed transmission mechanism for a compact vehicle capable of automatic transmission control,
an input shaft to which power is introduced from a power source;
a reduction gear connected to the input shaft;
a lavinyu planetary gear set connected to the reduction gear;
a loading camshaft branched from the input shaft;
a loading cam having one side connected to the loading camshaft; and
Including a clutch to which the other side and one side of the loading cam are connected,
The other side and the output shaft of the clutch are connected to the Lavinue planetary gear set, and the clutch is engaged and released by the operation of the loading cam according to the rotation speed of the input shaft. gearbox. According to claim 1,
The lavigne planetary gear set includes a first sun gear, a second sun gear, a carrier and a ring gear,
The first sun gear is connected to the reduction gear,
The ring gear is connected to the other side of the clutch,
The carrier is connected to the output shaft,
A two-speed transmission mechanism for a compact vehicle capable of automatic transmission, characterized in that it further comprises a first one-way clutch connected to the ring gear. According to claim 1,
The loading cam is
a first cam flange connected to the loading camshaft;
a second cam flange connected to one side of the clutch; and
a cam roller interposed between the first cam flange and the second cam flange,
wherein the first cam flange and the second cam flange are formed such that the cam roller moves outward as the rotational speed of the loading camshaft increases.

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