CROSS-REFERENCE TO RELATED APPLICATION

The present application claims priority to Korean Patent Application No. 10-2015-0170979, filed Dec. 2, 2015, the entire contents of which is incorporated herein for all purposes by this reference.

BACKGROUND OF THE INVENTION

Field of the Invention

The present invention relates to an automatic transmission for a vehicle. More particularly, the present invention relates to a planetary gear train of an automatic transmission for a vehicle that improves power delivery performance and fuel economy by achieving at least nine forward speed stages and widening speed ratio (or gear ratio) with a minimum number of constituent elements being used, and secures linearity of step ratios.

Description of Related Art

The recent increase in oil prices has caused car makers to meet global demands for improving fuel efficiency.

Therefore, research is being conducted on engines in terms of reducing weight and improving fuel efficiency by down-sizing, and research is also being conducted to ensure both drivability and competitiveness for maximizing fuel efficiency by implementing an automatic transmission with multiple speed stages.

However, in the case of the automatic transmission, the number of internal components is increased as the number of gear shift stages is increased, and as a result, the automatic transmission may be difficult to mount, the manufacturing cost and weight may be increased, and power transmission efficiency may be deteriorated.

Accordingly, development of a planetary gear train which may achieve maximum efficiency with a small number of components may be important in order to increase a fuel economy enhancement effect through the multiple-speeds.

In this aspect, in recent years, 8-speed automatic transmissions tend to be implemented and the research and development of a planetary gear train capable of implementing more speed stages has also been actively conducted.

However, since a conventional 8-speed automatic transmission has gear ratio span of 6.5-7.5, improvement of power performance and fuel economy may not be great.

In addition, if an 8-speed automatic transmission has a gear ratio span larger than 9.0, it is hard to secure linearity of step ratios. Therefore, driving efficiency of an engine and drivability of a vehicle may be deteriorated, and thus, development of high efficiency automatic transmissions which achieve at least nine forward speed stages is necessary.

The information disclosed in this Background of the Invention section is only for enhancement of understanding of the general background of the invention and should not be taken as an acknowledgement or any form of suggestion that this information forms the prior art already known to a person skilled in the art.

BRIEF SUMMARY

Various aspects of the present invention are directed to providing a planetary gear train of an automatic transmission for a vehicle having advantages of improving power delivery performance and fuel economy by achieving nine forward speed stages and one reverse speed stage, and widening gear ratio span and of securing linearity of step ratios.

According to various aspects of the present invention, a planetary gear train of an automatic transmission for a vehicle may include an input shaft receiving torque of an engine, an output shaft outputting changed torque of the engine, a first planetary gear set including first, second, and third rotation elements, a second planetary gear set including fourth, fifth, and sixth rotation elements, a third planetary gear set including seventh, eighth, and ninth rotation elements, and a fourth planetary gear set including tenth, eleventh, and twelfth rotation elements, in which the input shaft may be directly connected to the third rotation element, the second rotation element may be directly connected to the eleventh rotation element, the output shaft may be directly connected to the second rotation element, the third rotation element may be directly connected to the fourth rotation element, the sixth rotation element may be directly connected to the eighth rotation element, the ninth rotation element may be directly connected to the tenth rotation element, and the fifth rotation element may be selectively connected to a transmission housing.

The seventh rotation element may be selectively connected to the transmission housing, the twelfth rotation element may be selectively connected to the transmission housing, the input shaft may be selectively connected to the fifth rotation element, the ninth rotation element may be selectively connected to the fifth rotation element, and the first rotation element may be selectively connected to the twelfth rotation element.

The first, second, and third rotation elements may be a first sun gear, a first planet carrier, and a first ring gear, the fourth, fifth, and sixth rotation elements may be a second sun gear, a second planet carrier, and a second ring gear, the seventh, eighth, and ninth rotation elements may be a third sun gear, a third planet carrier, and a third ring gear, and the tenth, eleventh, and twelfth rotation elements may be a fourth sun gear, a fourth planet carrier, and a fourth ring gear.

The planetary gear train may further include a first clutch selectively connecting the input shaft with the fifth rotation element, a second clutch selectively connecting the ninth rotation element with the fifth rotation element, a third clutch selectively connecting the first rotation element with the twelfth rotation element, a first brake selectively connecting the fifth rotation element with the transmission housing, a second brake selectively connecting the seventh rotation element with the transmission housing, and a third brake selectively connecting the twelfth rotation element with the transmission housing.

According to various aspects of the present invention, a planetary gear train of an automatic transmission for a vehicle may include an input shaft receiving torque of an engine, an output shaft outputting changed torque, a first planetary gear set including first, second, and third rotation elements, a second planetary gear set including fourth, fifth, and sixth rotation elements, a third planetary gear set including seventh, eighth, and ninth rotation elements, a fourth planetary gear set including tenth, eleventh, and twelfth rotation elements, a first rotation shaft directly connected to the first rotation element, a second rotation shaft directly connecting the second rotation element with the eleventh rotation element and directly connected to the output shaft, a third rotation shaft directly connecting the third rotation element with the fourth rotation element and directly connected to the input shaft, a fourth rotation shaft directly connected to the fifth rotation element and selectively connected to the input shaft or a transmission housing, a fifth rotation shaft directly connecting the sixth rotation element with the eighth rotation element, a sixth rotation shaft directly connected to the seventh rotation element and selectively connected to the transmission housing, a seventh rotation shaft directly connecting the ninth rotation element with the tenth rotation element and selectively connected to the fourth rotation shaft, and an eighth rotation shaft directly connected to the twelfth rotation element and selectively connected to the first rotation shaft or the transmission housing.

The first planetary gear set may be a single pinion planetary gear set, the first rotation element may be a first sun gear, the second rotation element may be a first planet carrier, and the third rotation element may be a first ring gear, the second planetary gear set may be a single pinion planetary gear set, the fourth rotation element may be a second sun gear, the fifth rotation element may be a second planet carrier, and the sixth rotation element may be a second ring gear, the third planetary gear set may be a single pinion planetary gear set, the seventh rotation element may be a third sun gear, the eighth rotation element may be a third planet carrier, and the ninth rotation element may be a third ring gear, and the fourth planetary gear set may be a single pinion planetary gear set, the tenth rotation element may be a fourth sun gear, the eleventh rotation element may be a fourth planet carrier, and the twelfth rotation element may be a fourth ring gear.

The planetary gear train may further include a first clutch selectively connecting the input shaft with the fourth rotation shaft, a second clutch selectively connecting the fourth rotation shaft with the seventh rotation shaft, a third clutch selectively connecting the first rotation shaft with the eighth rotation shaft, a first brake selectively connecting the fourth rotation shaft with the transmission housing, a second brake selectively connecting the sixth rotation shaft with the transmission housing, and a third brake selectively connecting the eighth rotation shaft with the transmission housing.

The second clutch and the second and third brakes may be operated at a first forward speed stage, the first and second clutches and the third brake may be operated at a second forward speed stage, the first clutch and the second and third brakes may be operated at a third forward speed stage, the third clutch and the second and third brakes may be operated at a fourth forward speed stage, the first and third clutches and the second brake may be operated at a fifth forward speed stage, the first, second, and third clutches may be operated at a sixth forward speed stage, the second and third clutches and the second brake may be operated at a seventh forward speed stage, the second and third clutches and the first brake may be operated at an eighth forward speed stage, the third clutch and the first and second brakes may be operated at a ninth forward speed stage, and the first, second, and third brakes may be operated at a reverse speed stage.

According to various aspects of the present invention, a planetary gear train of an automatic transmission for a vehicle may include an input shaft receiving torque of an engine, an output shaft outputting changed torque of the engine, a first planetary gear set being a single pinion planetary gear set and including first, second, and third rotation elements, a second planetary gear set being a single pinion planetary gear set and including fourth, fifth, and sixth rotation elements, a third planetary gear set being a single pinion planetary gear set and including seventh, eighth, and ninth rotation elements, and a fourth planetary gear set being a single pinion planetary gear set and including tenth, eleventh, and twelfth rotation elements, a first rotation shaft directly connected to the first rotation element, a second rotation shaft directly connecting the second rotation element with the eleventh rotation element and directly connected to the output shaft, a third rotation shaft directly connecting the third rotation element with the fourth rotation element and directly connected to the input shaft, a fourth rotation shaft directly connected to the fifth rotation element and selectively connected to the input shaft or a transmission housing, a fifth rotation shaft directly connecting the sixth rotation element with the eighth rotation element, a sixth rotation shaft directly connected to the seventh rotation element and selectively connected to the transmission housing, a seventh rotation shaft directly connecting the ninth rotation element with the tenth rotation element and selectively connected to the fourth rotation shaft, an eighth rotation shaft directly connected to the twelfth rotation element and selectively connected to the first rotation shaft or the transmission housing, a first clutch selectively connecting the input shaft with the fourth rotation shaft, a second clutch selectively connecting the fourth rotation shaft with the seventh rotation shaft, a third clutch selectively connecting the first rotation shaft with the eighth rotation shaft, a first brake selectively connecting the fourth rotation shaft with the transmission housing, a second brake selectively connecting the sixth rotation shaft with the transmission housing, and a third brake selectively connecting the eighth rotation shaft with the transmission housing.

The first, second, and third rotation elements of the first planetary gear set may be a first sun gear, a first planet carrier, and a first ring gear, the fourth, fifth, and sixth rotation elements of the second planetary gear set may be a second sun gear, a second planet carrier, and a second ring gear, the seventh, eighth, and ninth rotation elements of the third planetary gear set may be a third sun gear, a third planet carrier, and a third ring gear, and the tenth, eleventh, and twelfth rotation elements of the fourth planetary gear set may be a fourth sun gear, a fourth planet carrier, and a fourth ring gear.

Various embodiments of the present invention may achieve at least nine forward speed stages and one reverse speed stage by combining four planetary gear sets with six control elements.

In addition, since a gear ratio span greater than 9.0 is secured, driving efficiency of the engine may be maximized.

In addition, since linearity of step ratios can be secured due to multiple speed stages, drivability such as acceleration before and after shift, rhythmical engine speed, and so on may be improved.

It is understood that the term â€œvehicleâ€ or â€œvehicularâ€ or other similar terms as used herein is inclusive of motor vehicles in general such as passenger automobiles including sports utility vehicles (SUV), buses, trucks, various commercial vehicles, watercraft including a variety of boats and ships, aircraft, and the like, and includes hybrid vehicles, electric vehicles, plug-in hybrid electric vehicles, hydrogen-powered vehicles and other alternative fuel vehicles (e.g., fuel derived from resources other than petroleum). As referred to herein, a hybrid vehicle is a vehicle that has two or more sources of power, for example, both gasoline-powered and electric-powered vehicles.

The methods and apparatuses of the present invention have other features and advantages which will be apparent from or are set forth in more detail in the accompanying drawings, which are incorporated herein, and the following Detailed Description, which together serve to explain certain principles of the present invention.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a schematic diagram of a planetary gear train according to an exemplary embodiment of the present invention.

FIG. 2 is an operation chart of control elements at each speed stage in the planetary gear train according to an exemplary embodiment of the present invention.

It should be understood that the appended drawings are not necessarily to scale, presenting a somewhat simplified representation of various features illustrative of the basic principles of the invention. The specific design features of the present invention as disclosed herein, including, for example, specific dimensions, orientations, locations, and shapes will be determined in part by the particular intended application and use environment.

DETAILED DESCRIPTION

Reference will now be made in detail to various embodiments of the present invention(s), examples of which are illustrated in the accompanying drawings and described below. While the invention(s) will be described in conjunction with exemplary embodiments, it will be understood that the present description is not intended to limit the invention(s) to those exemplary embodiments. On the contrary, the invention(s) is/are intended to cover not only the exemplary embodiments, but also various alternatives, modifications, equivalents and other embodiments, which may be included within the spirit and scope of the invention as defined by the appended claims.

FIG. 1 is a schematic diagram of a planetary gear train according to various embodiments of the present invention.

Referring to FIG. 1, a planetary gear train according to various embodiments of the present invention includes first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 disposed on the same axis, an input shaft IS, an output shaft OS, eight shafts TM1 to TM8 connected to at least one of rotation elements of the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4, three clutches C1 to C3 and three brakes B1 to B3 that are control elements, and a transmission housing H.

Torque input from the input shaft IS is changed by cooperation of the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4, and the changed torque is output through the output shaft OS.

The planetary gear sets are disposed in a sequence of the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 from an engine.

The input shaft IS is an input member and torque from a crankshaft of the engine is torque-converted through a torque converter to be input into the input shaft IS.

The output shaft OS is an output member, is disposed in parallel with the input shaft IS, and transmits driving torque to a driving wheel through a differential apparatus.

The first planetary gear set PG1 is a single pinion planetary gear set and includes a first sun gear S1, a first planet carrier PC1 rotatably supporting a first pinion P1 that is externally meshed with the first sun gear S1, and a first ring gear R1 that is internally meshed with the first pinion P1 respectively as first, second, and third rotation elements N1, N2, and N3.

The second planetary gear set PG2 is a single pinion planetary gear set and includes a second sun gear S2, a second planet carrier PC2 rotatably supporting a second pinion P2 that is externally meshed with the second sun gear S2, and a second ring gear R2 that is internally meshed with the second pinion P2 respectively as fourth, fifth, and sixth rotation elements N4, N5, and N6.

The third planetary gear set PG3 is a single pinion planetary gear set and includes a third sun gear S3, a third planet carrier PC3 rotatably supporting a third pinion P3 that is externally meshed with the third sun gear S3, and a third ring gear R3 that is internally meshed with the third pinion P3 respectively as seventh, eighth, and ninth rotation elements N7, N8, and N9.

The fourth planetary gear set PG4 is a single pinion planetary gear set and includes a fourth sun gear S4, a fourth planet carrier PC4 rotatably supporting a fourth pinion P4 that is externally meshed with the fourth sun gear S4, and a fourth ring gear R4 that is internally meshed with the fourth pinion P4 respectively as tenth, eleventh, and twelfth rotation elements N10, N11, and N12.

The second rotation element N2 is directly connected to the eleventh rotation element N11, the third rotation element N3 is directly connected to the fourth rotation element N4, the sixth rotation element N6 is directly connected to the eighth rotation element N8, and the ninth rotation element TM9 is directly connected to the tenth rotation element N10 such that the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 includes eight rotation shafts TM1 to TM8.

The eight shafts TM1 to TM8 will be described in further detail.

The first rotation shaft TM1 is connected to the first rotation element N1 (first sun gear S1).

The second rotation shaft TM2 directly connects the second rotation element N2 (first planet carrier PCI) with the eleventh rotation element N11 (fourth planet carrier PC4), and is directly connected to the output shaft OS so as to be operated as an output element.

The third rotation shaft TM3 directly connects the third rotation element N3 (first ring gear R1) with the fourth rotation element N4 (second sun gear S2), and is directly connected to the input shaft IS so as to be operated as an input element.

The fourth rotation shaft TM4 is connected to the fifth rotation element N5 (second planet carrier PC2), is selectively connected to the input shaft IS so as to be operated as a selective input element, and is selectively connected to the transmission housing H so as to be operated as a selective fixed element.

The fifth rotation shaft TM5 directly connects the sixth rotation element N6 (second ring gear R2) with the eighth rotation element N8 (third planet carrier PC3).

The sixth rotation shaft TM6 is connected to the seventh rotation element N7 (third sun gear S3) and is selectively connected to the transmission housing H so as to be operated as a selective fixed element.

The seventh rotation shaft TM7 directly connects the ninth rotation element N9 (third ring gear R3) with the tenth rotation element N10 (fourth sun gear S4) and is selectively connected to the fourth rotation shaft TM4.

The eighth rotation shaft TM8 is connected to the twelfth rotation element N12 (fourth ring gear R4), is selectively connected to the transmission housing H so as to be operated as a selective fixed element, and is selectively connected to the first rotation shaft TM1.

In addition, three clutches C1, C2, and C3 that are control elements are disposed at portions at which two rotation shafts among the rotation shafts TM1 to TM8 are selectively connected to each other.

In addition, three brakes B1, B2, and B3 that are control elements are disposed at portions at which any one rotation shaft among the rotation shafts TM1 to TM8 is selectively connected to the transmission housing H.

Arrangements of the six control elements C1 to C3 and B1 to B3 are described in detail.

The first clutch C1 is disposed between the input shaft IS and the fourth rotation shaft TM4 and selectively connects the input shaft IS with the fourth rotation shaft TM4.

The second clutch C2 is disposed between the fourth rotation shaft TM4 and the seventh rotation shaft TM7 and selectively connects the fourth rotation shaft TM4 with the seventh rotation shaft TM7.

The third clutch C3 is disposed between the first rotation shaft TM1 and the eighth rotation shaft TM8 and selectively connects the first rotation shaft TM1 with the eighth rotation shaft TM8.

The first brake B1 is disposed between the fourth rotation shaft TM4 and the transmission housing H and causes the fourth rotation shaft TM4 to be operated as a selective fixed element.

The second brake B2 is disposed between the sixth rotation shaft TM6 and the transmission housing H and causes the sixth rotation shaft TM6 to be operated as a selective fixed element.

The third brake B3 is disposed between the eighth rotation shaft TM8 and the transmission housing H and causes the eighth rotation shaft TM8 to be operated as a selective fixed element.

The control elements including the first, second, and third clutches C1, C2, and C3 and the first, second, and third brakes B1, B2, and B3 may be multi-plates friction elements of wet type that are operated by hydraulic pressure.

FIG. 2 is an operation chart of control elements at each speed stage in the planetary gear train according to various embodiments of the present invention.

As shown in FIG. 2, three control elements are operated at each speed stage in the planetary gear train according to various embodiments of the present invention.

The second clutch C2 and the second and third brakes B2 and B3 are simultaneously operated at a first forward speed stage D1. In a state that the fourth rotation shaft TM4 is connected to the seventh rotation shaft TM7 by operation of the second clutch C2, torque of the input shaft IS is input to the third rotation shaft TM3. In addition, the sixth and eighth rotation shafts TM6 and TM8 are operated as the fixed elements by operation of the second and third brakes B2 and B3. Therefore, the torque of the input shaft IS is shifted into the first forward speed stage, and the first forward speed stage is output through the output shaft OS connected to the second rotation shaft TM2.

The first and second clutches C1 and C2 and the third brake B3 are simultaneously operated at a second forward speed stage D2. In a state that the input shaft IS is connected to the fourth rotation shaft TM4 by operation of the first clutch C1 and the fourth rotation shaft TM4 is connected to the seventh rotation shaft TM7 by operation of the second clutch C2, the torque of the input shaft IS is input to the third rotation shaft TM3 and the fourth rotation shaft TM4. In addition, the eighth rotation shaft TM8 is operated as the fixed element by operation of the third brake B3. Therefore, the torque of the input shaft IS is shifted into the second forward speed stage, and the second forward speed stage is output through the output shaft OS connected to the second rotation shaft TM2.

The first clutch C1 and the second and third brakes B2 and B3 are simultaneously operated at a third forward speed stage D3. In a state that the input shaft IS is connected to the fourth rotation shaft TM4 by operation of the first clutch C1, the torque of the input shaft IS is input to the third rotation shaft TM3 and the fourth rotation shaft TM4. In addition, the sixth and eighth rotation shafts TM6 and TM8 are operated as the fixed elements by operation of the second and third brakes B2 and B3. Therefore, the torque of the input shaft IS is shifted into the third forward speed stage, and the third forward speed stage is output through the output shaft OS connected to the second rotation shaft TM2.

The third clutch C3 and the second and third brakes B2 and B3 are simultaneously operated at a fourth forward speed stage D4. In a state that the first rotation shaft TM1 is connected to the eighth rotation shaft TM8 by operation of the third clutch C3, the torque of the input shaft IS is input to the third rotation shaft TM3. In addition, the sixth and eighth rotation shafts TM6 and TM8 are operated as the fixed elements by operation of the second and third brakes B2 and B3. Therefore, the torque of the input shaft IS is shifted into the fourth forward speed stage, and the fourth forward speed stage is output through the output shaft OS connected to the second rotation shaft TM2.

The first and third clutches C1 and C3 and the second brake B2 are simultaneously operated at a fifth forward speed stage D5. In a state that the input shaft IS is connected to the fourth rotation shaft TM4 by operation of the first clutch C1 and the first rotation shaft TM1 is connected to the eighth rotation shaft TM8 by operation of the third clutch C3, the torque of the input shaft IS is input to the third rotation shaft TM3 and the fourth rotation shaft TM4. In addition, the sixth rotation shaft TM6 is operated as the fixed element by operation of the second brake B2. Therefore, the torque of the input shaft IS is shifted into the fifth forward speed stage, and the fifth forward speed stage is output through the output shaft OS connected to the second rotation shaft TM2.

The first, second, and third clutches C1, C2, and C3 are simultaneously operated at a sixth forward speed stage D6. In a state that the input shaft IS is connected to the fourth rotation shaft TM4 by operation of the first clutch C1, the fourth rotation shaft TM4 is connected to the seventh rotation shaft TM7 by operation of the second clutch C2, and the first rotation shaft TM1 is connected to the eighth rotation shaft TM8 by operation of the third clutch C3, the torque of the input shaft IS is input to the third rotation shaft TM3 and the fourth rotation shaft TM4. In this case, the first, second, third, and fourth planetary gear sets PG1, PG2, PG3, and PG4 become lock-up states, the torque of the input shaft IS is shifted into the sixth forward speed stage, and the sixth forward speed stage is output through the output shaft OS connected to the second rotation shaft TM2.

The second and third clutches C2 and C3 and the second brake B2 are simultaneously operated at a seventh forward speed stage D7. In a state that the fourth rotation shaft TM4 is connected to the seventh rotation shaft TM7 by operation of the second clutch C2 and the first rotation shaft TM1 is connected to the eighth rotation shaft TM8 by operation of the third clutch C3, the torque of the input shaft IS is input to the third rotation shaft TM3. In addition, the sixth rotation shaft TM6 is operated as the fixed element by operation of the second brake B2. Therefore, the torque of the input shaft IS is shifted into the seventh forward speed stage, and the seventh forward speed stage is output through the output shaft OS connected to the second rotation shaft TM2.

The second and third clutches C2 and C3 and the first brake B1 are simultaneously operated at an eighth forward speed stage D8. In a state that the fourth rotation shaft TM4 is connected to the seventh rotation shaft TM7 by operation of the second clutch C2 and the first rotation shaft TM1 is connected to the eighth rotation shaft TM8 by operation of the third clutch C3, the torque of the input shaft IS is input to the third rotation shaft TM3. In addition, the fourth rotation shaft TM4 is operated as the fixed element by operation of the first brake B1. Therefore, the torque of the input shaft IS is shifted into the eighth forward speed stage, and the eighth forward speed stage is output through the output shaft OS connected to the second rotation shaft TM2.

The third clutch C3 and the first and second brakes B1 and B2 are simultaneously operated at a ninth forward speed stage D9. In a state that the first rotation shaft TM1 is connected to the eighth rotation shaft TM8 by operation of the third clutch C3, the torque of the input shaft IS is input to the third rotation shaft TM3. In addition, the fourth and sixth rotation shafts TM4 and TM6 are operated as the fixed elements by operation of the first and second brakes B1 and B2. Therefore, the torque of the input shaft IS is shifted into the ninth forward speed stage, and the ninth forward speed stage is output through the output shaft OS connected to the second rotation shaft TM2.

The first, second, and third brakes B1, B2, and B3 are simultaneously operated at a reverse speed stage REV. In a state that the torque of the input shaft IS is input to the third rotation shaft TM3, the fourth, sixth, and eighth rotation shafts TM4, TM6, and TM8 are operated as the fixed elements by operation of the first, second, and third brakes B1, B2, and B3. Therefore, the torque of the input shaft IS is shifted into the reverse speed stage, and the reverse speed stage is output through the output shaft OS connected to the second rotation shaft TM2.

The planetary gear train according various embodiments of the present invention may achieve at least nine forward speed stages and one reverse speed stage by combining four planetary gear sets PG1, PG2, PG3, and PG4 with the three clutches C1, C2, and C3 and the three brakes B1, B2, and B3.

In addition, since a gear ratio span greater than 9.0 is secured, driving efficiency of the engine may be maximized.

In addition, since linearity of step ratios can be secured due to multiple speed stages, drivability such as acceleration before and after shift, rhythmical engine speed, and on the like may be improved.

The foregoing descriptions of specific exemplary embodiments of the present invention have been presented for purposes of illustration and description. They are not intended to be exhaustive or to limit the invention to the precise forms disclosed, and obviously many modifications and variations are possible in light of the above teachings. The exemplary embodiments were chosen and described in order to explain certain principles of the invention and their practical application, to thereby enable others skilled in the art to make and utilize various exemplary embodiments of the present invention, as well as various alternatives and modifications thereof. It is intended that the scope of the invention be defined by the Claims appended hereto and their equivalents.