FIELD OF THE INVENTION
The invention relates to power tools, and more particularly to power tool transmissions.
BACKGROUND OF THE INVENTION
Power tool transmissions are often user-configurable to provide different speed outputs of the power tool. For example, an operator of a multi-speed drill may configure the drill for high-speed operation or low-speed operation by actuating a switch on the drill.
SUMMARY OF THE INVENTION
The invention provides, in one aspect, a multi-stage planetary transmission powered by an electric motor having an output pinion. The multi-stage planetary transmission includes a transmission housing and a first planetary stage at least partially positioned in the transmission housing. The first planetary stage includes a first stage ring gear, a first stage carrier, and a plurality of first stage planet gears supported by the first stage carrier. The motor output pinion is engaged with each of the first stage plant gears. The transmission further includes a second planetary stage positioned downstream of the first planetary stage to receive torque from the first planetary stage and a shift mechanism operable to move the first stage ring gear between a first position, in which the first stage ring gear is rotatably fixed relative to the transmission housing for enabling the first planetary stage, and a second position, in which the first stage ring gear is coupled for co-rotation with the first stage carrier for disabling the first planetary stage.
The invention provides, in another aspect, a rotary power tool including an electric motor having an output pinion, a bit retainer in which a tool bit is receivable, and a multi-stage planetary transmission coupling the motor and the bit retainer. The multi-stage planetary transmission includes a transmission housing and a first planetary stage at least partially positioned in the transmission housing. The first planetary stage includes a first stage ring gear, a first stage carrier, and a plurality of first stage planet gears supported by the first stage carrier. The motor output pinion is engaged with each of the first stage plant gears. The transmission further includes a second planetary stage positioned downstream of the first planetary stage to receive torque from the first planetary stage and a shift mechanism operable to move the first stage ring gear between a first position, in which the first stage ring gear is rotatably fixed relative to the transmission housing for enabling the first planetary stage, and a second position, in which the first stage ring gear is coupled for co-rotation with the first stage carrier for disabling the first planetary stage.
Other features and aspects of the invention will become apparent by consideration of the following detailed description and accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
FIG. 1 is a side view of rotary power tool.
FIG. 2 is a cross-sectional view of a multi-stage planetary transmission for use in the power tool of FIG. 1 configured for operation in a low-speed, high-torque mode.
FIG. 3 is a cross-sectional view of the transmission of FIG. 2 configured for operation in a high-speed, low-torque mode.
Before any embodiments of the invention are explained in detail, it is to be understood that the invention is not limited in its application to the details of construction and the arrangement of components set forth in the following description or illustrated in the following drawings. The invention is capable of other embodiments and of being practiced or of being carried out in various ways. Also, it is to be understood that the phraseology and terminology used herein is for the purpose of description and should not be regarded as limiting.
DETAILED DESCRIPTION
FIG. 2 illustrates a multi-stage planetary transmission 10 for use with a rotary power tool 12 (e.g., a drill, etc.; FIG. 1). An output of the transmission 10 (FIG. 2) is coupled to an output shaft 18 which, in turn, may be coupled to a conventional tool chuck or bit retainer 20 (FIG. 1) in a conventional manner. An adjustable clutch mechanism 22 (FIG. 2) may also be used in conjunction with the transmission 10 to selectively limit the amount of torque that may be transferred from the transmission 10 to the output shaft 18, the operational details of which are described in detail below. However, the transmission 10 need not be used in conjunction with the adjustable clutch mechanism 22.
With continued reference to FIG. 2, the transmission 10 includes a transmission housing 26 and three planetary stages 30, 34, 38, the last of which is coupled to the output shaft 18. In the illustrated construction of the transmission 10, the transmission housing 26 includes a rear housing portion 42 containing therein the three planetary stages 30, 34, 38, a front housing portion 46 through which the output shaft 18 extends, and an end cap 50 coupled to the rear housing portion 42. Alternatively, the transmission housing 26 may be divided into any number of portions, or may be configured as a substantially unitary structure. The end cap 50 also provides a mount 54 to which an electric motor 56 (FIG. 1) may be coupled.
With reference to FIG. 2, the first planetary stage 30 includes a first stage ring gear 62, a first stage carrier 66, and a plurality of first stage planet gears 70. With continued reference to FIG. 2, the first stage carrier 66 includes a sun gear 74, which is a component of the second planetary stage 34, extending from the front of the carrier 66. A plurality of axles (not shown) also extend from the rear of the carrier 66 upon which the first stage planet gears 70 are rotatably supported. The first stage carrier 66 also includes a plurality of projections 78 that extend radially outwardly from an outer circumferential surface 82 of the carrier 66, the purpose of which is described below. The first stage planet gears 70 are engaged to an input pinion 84 which, in turn, is coupled to the output shaft of the motor for transferring torque to the three planetary stages 30, 34, 38.
With reference to FIG. 3, the first stage ring gear 62 is annular and has a plurality of teeth 86 on an inner circumferential surface 90 of the ring gear 62 that are selectively meshed with the plurality of first stage planet gears 70. The first stage ring gear 62 also includes a plurality of teeth 94 on an outer circumferential surface 98 of the ring gear 62 that are engageable with corresponding teeth 102 on the inner peripheral surface of the end cap 50. The outer circumferential surface 98 of the first stage ring gear 62 is cylindrical to enable to the first stage ring gear 62 to selectively rotate within the transmission housing 26.
With reference to FIG. 2, the second planetary stage 34 includes a second stage carrier 106 and a plurality of second stage planet gears 110. Likewise, the third planetary stage 38 includes a third carrier 114 and a plurality of third stage planet gears 118. The second planetary stage 34 and the third planetary stage 38 share a common ring gear 122. The second planetary stage 34 is positioned downstream of the first planetary stage 30 to receive torque from the first planetary stage 30. Likewise, the third planetary stage 38 is positioned downstream of the second planetary stage 34 to receive torque from the second planetary stage 34.
The third carrier 114 is directly coupled to the output shaft 18. The third carrier 114 may be coupled to the output shaft 18 in any of a number of different ways (e.g., by using a key and keyway arrangement, an interference fit, a spline-fit, etc.)
With continued reference to FIG. 2, the common ring gear 122 is annular and has a plurality of teeth 126 on an inner circumferential surface 130 of the common ring gear 122 that mesh with the plurality of second stage planet gears 110 and the plurality of third stage planet gears 118. An outer circumferential surface 134 of the common ring gear 122 is cylindrical to enable the common ring gear 122 to selectively rotate within the transmission housing 26. A plurality of clutch dogs or ramps (not shown) extend from a front end 138 of the common ring gear 122 for engagement with the clutch mechanism 22. The clutch mechanism 22 allows the common ring gear 122 to rotate within the transmission housing 26 in response to the output shaft 18 seizing as a result of a reaction torque being applied to the output shaft 18 by a workpiece (e.g., a fastener) substantially equal to the torque setting of the clutch mechanism 22.
With reference to FIGS. 2 and 3, the transmission 10 further includes a shift mechanism 142 operable to move the first stage ring gear 62 between a first position (FIG. 2), in which the first stage ring gear 62 is rotatably fixed relative to the transmission housing 26 for enabling the first planetary stage 30, and a second position (FIG. 3), in which the first stage ring gear 62 is coupled for co-rotation with the first stage carrier 66 for disabling the first planetary stage 30. In the illustrated construction of the transmission 10, the shift mechanism 142 includes a linearly movable shuttle 146 for shifting the first stage ring gear 62 between first and second positions. Alternatively, the shift mechanism 142 may be configured in any of a number of different ways for displacing the first stage ring gear 62 between the first and second positions.
Operation of the multi-speed planetary transmission 10 will now be discussed with respect to FIGS. 2 and 3.
FIG. 2 illustrates the multi-stage planetary transmission 10 configured in a low-speed, high torque mode. In this mode, the shuttle 146 and first stage ring gear 62 are shifted to the first position (i.e., to the left as shown in FIG. 2), thereby engaging the respective teeth 86, 102 on the first stage ring gear 62 and the end cap 50 (FIG. 3) to inhibit relative rotation between the first stage ring gear 62 and the transmission housing 26. The first stage ring gear 62 is also engaged with the plurality of first stage planet gears 70 in the first position. The first stage ring gear 62 remains fixed relative to the transmission housing 26 to enable the first planetary stage 30.
FIG. 3 illustrates the multi-stage planetary transmission 10 in a high-speed, low torque mode. In this mode, the shuttle 146 and the first stage ring gear 62 are shifted to the second position (i.e., to the right as shown in FIG. 3), thereby disengaging the first stage ring gear 62 from the end cap 50 and engaging the respective teeth 86, 78 of the first stage ring gear 62 and the first stage carrier 66. In this position, the first stage ring gear 62 co-rotates with the first stage carrier 66 for disabling the first planetary stage 30. It should also be understood that when the first stage ring gear 62, when in the second position, rotationally interlocks the motor output shaft with all of the components of the first planetary stage 30 and the second stage sun gear 74 extending from the first stage carrier 66.
Various features of the invention are set forth in the following claims.
Patent Application
20140080659
