Variable speed power transmission apparatus

Abstract: A variable speed power transmission apparatus comprises an epicycle reduction gear device that has planetary gears (11) whose shafts (12) are supported at equal intervals taken circumferentially thereof by carriers (9) fixed to an output shaft (8) thereof, the planetary gears (11) being meshed between external teeth of a sun gear (4) fixed to an input shaft (1) connected to a drive source and internal teeth of a ring gear (7), and a variable speed hydraulic driver system (3,6) that is driven by an oil pressure generated by a power of the drive source in such a way as to be variably and reversibly rotated by the oil pressure. An output shaft of the variable speed oil pressure driver system (6) is connected to the ring gear (7) in interlocking relation therewith to thereby cause forward rotation, reverse rotation or stoppage of the ring gear (7) by the variable speed hydraulic driver system. Whereby, non-step change is made of the speed of the ring gear (7). Since the invention has been constructed as mentioned above, the invention makes it possible to obtain a variable speed power transmission apparatus which enables highly efficient non-step change in the rotation speed thereof over a wide range of rotations numbers without being increased in size and in cost.

Description: Background of the Invention Field of the Invention The present invention relates to a variable speed power transmission apparatus as defined in the preamble portion of claim 1 which is applicable to each of rotating machines such as drivers for driving a blower, pump, compressor, centrifugal separator, stirrer, mill, excavator, cutter machine, polishing machine, winch, crane hoister and automobile collision tester and which is intended to be used for making variable the output rotation number of the rotating machine. Description of the Related Art While almost all of rotating machines such as drivers for driving a blower, pump, compressor, centrifugal separator, stirrer, mill, excavator, polishing machine, winch, crane hoister and automobile collision tester have each been used with their fixed rotation number, when using each of these rotating machines with the output rotation number thereof being kept variable, the following means have hitherto been adopted. (1) Use is made of a rotating machine that has been prepared by using an AC (Alternating Current) motor and an inverter in combination, or by using a DC (Direct Current) motor and a thyristor in combination. In this case, it becomes necessary to use an installation space for installing a controller device for controlling the inverter or thyristor, with the result that the size of the rotating machine is increased. In addition, since it is needed to maintain the temperature of the installation space (control chamber or the like) for installing the controller device to be at a fixed value, it is needed to use an air conditioner equipment, with the result that the size of the rotating machine is further increased and in addition the facilities involved therein become high in cost. (2) Use is made of a rotating machine that has been prepared by using concurrently used AC/DC motors, hydraulic pump and hydraulic motor in combination, or by using an engine, hydraulic pump and hydraulic motor in combination. In this case, although a wide range of variable speeds is obtained, the efficiency becomes low and the power consumption increases. The basic structure of a variable speed power transmission apparatus with the features of the preamble portion of claim 1 is known from DE 92 08 554 U or EP-0 137 406 A. In these devices an epicycle reduction gear device is combined with a variable speed hydraulic driver system so as to rotate a ring gear of the reduction gear device in alternating directions or to fix the ring gear. Summary of the Invention The object of the present invention is to provide a variable speed power transmission apparatus which is protected with respect to damages resulting from excessive torque. The present invention provides a variable speed power transmission apparatus comprising an epicycle reduction gear device that has planetary gears whose shafts are supported at equal intervals taken circumferentially thereof by carriers fixed to an output shaft thereof, the planetary gears being meshed between external teeth of a sun gear fixed to an input shaft for receiving a torque from a drive source and internal teeth of a ring gear, and a variable speed hydraulic driver system that is adapted to be driven by an oil pressure in such a way as to be variably and reversibly rotated by the oil pressure, an output shaft of the variable speed hydraulic driver system being connected to the ring gear in interlocking relation therewith to thereby cause forward rotation, reverse rotation or stoppage of the ring gear by the variable speed hydraulic driver system, wherein the variable speed hydraulic driver system comprises a variable amount of discharge type hydraulic pump and a variable speed and reversible rotation type hydraulic motor that is driven by a pressure oil supplied from the hydraulic pump, characterized in that an output shaft of the hydraulic motor has a worm fixed thereto, the worm being meshed with a worm wheel that is connected to the ring gear, whereby the ring gear is forward rotated, reverse rotated or stopped by the hydraulic motor. Accordingly, according to the present invention, when an overload has acted on the output shaft side, this overload is supported by the worm mechanism composed of the worm and the worm wheel. By the reverse rotation prevention action of this worm mechanism, it is possible to prevent the overload from acting on the hydraulic motor. In a preferred embodiment a transmission is provided through which a torque is input from the drive source to the input shaft, and a hydraulic transmission to which the torque is input from an output end of the drive source through a transmission path that branches off from a transmission path that leads to the transmission, an output shaft of the hydraulic transmission being interlockingly connected to the ring gear by means of the worm mechanism to thereby cause forward rotation, reverse rotation or stoppage of the ring gear by the hydraulic transmission. Accordingly, according to this embodiment, the torque from the drive source that operates with a fixed number of rotations is on one hand transmitted to the input shaft of the epicycle reduction gear device through the transmission of mechanical or the like's type and is on the other hand transmitted to the ring gear of the epicycle reduction gear device through the hydraulic transmission and worm mechanism to thereby cause a change in the output rotations number of the hydraulic transmission while causing forward rotation or reverse rotation of it. Also, by making "off" the output of the hydraulic transmission, the rotation of the ring gear is changed while keeping this ring gear in a state of its being forward rotated or reverse rotated, or is stopped. Accordingly, by simultaneously controlling the rotation number of the input shaft and the rotation number of the ring gear as in the first embodiment, in both the forward rotation and the reverse rotation of the ring gear non-step control thereof can be made over a wider range of rotation numbers. Further, since the worm mechanism has been interposed between the output end of the hydraulic transmission and the ring gear, when an overload has acted on the output shaft side, this overload is undertaken by this worm mechanism through the reverse rotation prevention action based on the combination of the worm and the worm wheel. Whereby, it is possible to prevent the overload from being transmitted to the hydraulic transmission. A further embodiment is an arrangement wherein, in each of the other embodiments, the ring gear has additionally provided thereon a brake for stopping the rotation of this ring gear. Accordingly, according to this embodiment, when inconveniences such as malfunction of the hydraulic pump, hydraulic motor, hydraulic transmission or the like, oil leakage from the oil piping, etc. have occurred in the hydraulic system, the brake is operated to thereby stop the rotation of the ring gear. As a result, there is formed a speed reduction system of a fixed speed reduction ratio wherein the ring gear of the epicycle reduction gear device has been fixed, with the result that the output shaft is rotated with a prescribed fixed number of rotations. Also, if the brake is released, non-step speed change operation that is similar to that which is performed in the other embodiments can be realized. As mentioned above, according to the present invention, the following effects can be procured. By causing forward rotation, reverse rotation or stoppage of the ring gear of the epicycle reduction gear device by a variable speed hydraulic driver system such as a hydraulic pump and hydraulic motor, hydraulic transmission, etc., the rotation of the output shaft can be changed in non-step manner over a wide range of rotations numbers. Accordingly, it becomes unnecessary to use an inverter or thyristor that is used in the conventional means which uses an AC motor or DC motor. In addition, it becomes also unnecessary to use an air conditioner equipment for a space that is used to install therewithin a controller device for controlling each of these parts. As a result, it is possible to realize reduction in size and cost of the apparatus. Also, since the ring gear of the epicycle reduction gear device is only rotated by the combined system of the hydraulic pump and hydraulic motor or by the hydraulic transmission, the power consumption is small, with the result that remarkable rise in the efficiency -can be achieved compared to the conventional power transmission apparatus that uses the hydraulic pump that is driven by an engine or power driven motor and the hydraulic motor. Brief Description of the Drawings Fig. 1 is a perspective view illustrating the outer appearance of a variable speed power transmission apparatus according to a first example for explaining certain features of the present invention; Fig. 2 is a perspective view illustrating the outer appearance of the structure of a variable speed power transmission apparatus according to a second example ; Figs. 3(A) and 3(B) are both enlarged perspective views illustrating a brake mount portion of a ring gear according to the second example; Fig. 4 is an enlarged outer appearance view illustrating the structure of the clutch mount portion according to the second example illustrated in Fig. 2; Fig. 5 is a perspective view illustrating the outer appearance of a variable speed power transmission apparatus according to a third example for explaining certain features of the present invention; Fig. 6 is a perspective view illustrating the outer appearance of a variable speed power transmission apparatus according to a fourth example for explaining certain features of the present invention; Fig. 7 is a sectional view illustrating a variable speed power transmission apparatus according to a first embodiment of the present invention; Fig. 8 is a constructional view illustrating a variable speed power transmission apparatus according to a second embodiment of the present invention; and Fig. 9 is a constructional view illustrating a variable speed power transmission apparatus according to a third embodiment of the present invention. Detailed Description of the Preferred Embodiments In Fig. 1 that illustrates a first example to explain the present invention, a reference numeral 1 denotes an input shaft, a reference numeral 100 denotes a differential epicycle reduction gear device, and a reference numeral 8 denotes an output shaft. A reference numeral 4 denotes a sun gear of the epicycle reduction gear device that has been secured to an end portion of the input shaft 1, a reference numeral 7 denotes a ring gear of the epicycle reduction gear device 100, a reference numeral 9 denotes carriers of the epicycle reduction gear device 100 that have been fixed to the output shaft 8, a reference numeral 12 denotes a plurality (three in this example) of planet shafts that are fixed to the carriers 9 at equal intervals taken in the circumferential direction of the epicycle reduction gear device 100, and a reference numeral 11 denotes planetary gears whose shafts are supported by the planet shafts 12 respectively and which are meshed with external teeth of the sun gear 4 and internal teeth of the ring gear 7. A reference numeral 3 denotes a variable amount of discharge type hydraulic pump and a reference numeral 6 denotes a variable speed and reversible rotation type hydraulic motor that is driven by a pressure oil that is forcedly supplied from the hydraulic pump 3 through an oil pipe 5. To the input shaft 1 there is secured an input shaft gear 13 which is meshed with a pump driving gear 2 that is fixed to an input shaft of the hydraulic pump 3, whereby the hydraulic pump is driven by the torque of the input shaft 1. A reference numeral 14 denotes an input gear that has been fixed to the output shaft of the hydraulic motor 6. The input gear 14 is meshed with external teeth 7a of the ring gear 7 of the epicycle reduction gear device 100. As a result, the epicycle reduction gear device 100 is equipped with two input systems, one of which is a first input system having its torque input from the input shaft 1 to the sun gear 4 and the other of which is a second input system having its torque input from the input gear 14 of the hydraulic motor 6 to the ring gear 7. The operation of the variable speed power transmission apparatus that has been constructed as mentioned above will now be explained. The torque of the input shaft is transmitted to the variable amount of discharge type hydraulic pump 3 through the input shaft gear 13 and pump driving gear 2 to thereby drive the hydraulic pump 3. The pressure oil that has been discharged from the hydraulic pump 3 is supplied to the hydraulic motor 6 by way of the oil pipe 5, whereby the hydraulic motor 6 is driven for rotation. In the driving system having the hydraulic pump 3 and hydraulic motor 6 used in combination, when the amount of discharge of the hydraulic pump 3 is varied through electric control or manually, the number of rotations of the hydraulic motor 6 is varied and, since this hydraulic motor 6 is reversible, the rotation direction thereof also is varied. Accordingly, it results that the rotational force or torque of this hydraulic motor 6 is input to the ring gear 7 through the input gear 14. Whereby, the ring gear 7 is forward rotated, reverse rotated or stopped (made stationary). On the other hand, the torque of the input shaft 1 is input to the sun gear 4 of the epicycle reduction gear device 100 and is transmitted from this sun gear 4 to the output shaft 8 through the planetary gears 11 each making its rotation around the sun gear 4 while making its rotation about its own axis between the sun gear 4 and internal teeth 7b of the ring gear 7 and then through the carriers 9. In the power transmission system illustrated in Fig. 1, when the hydraulic pump 3 is stopped, the hydraulic motor also is stopped, whereby the rotation of the ring gear 7 is stopped through the input gear 14 and as a result the ring gear 7 is brought to a state of its being made stationary. In this case, the rotation of the input shaft 1 is transmitted to the output shaft 8 through the sun gear 4, planet gears 11 and carriers 9 that are combined with each other into an ordinary epicycle reduction gear device form by having its speed reduced to a number of rotations that is determined according to the teeth numbers of the respective gears. Also, when the ring gear 7 is caused to make a rotation that is reverse from that of the output shaft 8 by the hydraulic motor 6, the rotation number that is transmitted from the carriers 9 to the output shaft 8 is more decreased than the rotation number which, when the ring gear 7 is in a state of its being stopped (made stationary), is transmitted thereto. Further, when the ring gear 7 is rotated in the same direction as that of the output shaft 8 by the hydraulic motor 6, conversely to the above the rotation number of the output shaft 8 is increased and hence the speed thereof is more increased than that which is when the ring gear is kept stationary. In the first example illustrated in Fig. 1, when the rotation number of the input shaft 1 is changed and it is wanted to restore the rotation number of the output shaft 8 to a target rotation number, it is arranged to change the amount of discharge of the hydraulic pump 3, to thereby cause the forward rotation, stoppage or reverse rotation of the hydraulic motor 6, to thereby cause the forward rotation, stoppage or reverse rotation of the ring gear 7, and to thereby cause the restoration and maintenance of the rotation of each of the carriers 9 and output shaft 8 to and at the target rotation number. In this first example, as mentioned above, by controlling the state of discharge of the hydraulic pump 3 and thereby causing the forward rotation, stoppage or reverse rotation of the hydraulic pump 6 and thereby causing a change in the forward or reverse rotation number, or stoppage, of the ring gear 7 of the differential epicycle reduction gear device 100, it is possible to cause non-step change in the rotation number of the output shaft 8. In a second example to explain of the present invention that is illustrated in Figs. 2 to 4, on an outer periphery of the ring gear 7 there is mounted a brake 10 for braking this ring gear 7 and, on the other hand, as illustrated in Fig. 4, a clutch 12 is interposed between the pump driving gear 2 and the hydraulic pump 3. The type of this brake 10 includes a disk brake system wherein, as illustrated in Fig. 3(A), a disk 7c whose diameter has been increased by the quantity needed to brake the rotation of the ring gear 7 is provided on one side (e.g., output shaft side) of this ring gear 7 and this disk 7c is clamped for brake, or a disk brake system wherein, as illustrated in Fig. 3(B), the ring gear 7 is clamped from both sides thereof by means of pads, etc. The remaining construction of this second example is the same as that of the first example and therefore the same members or components are denoted by the same reference symbols. In Figs. 2 to 4, during an ordinary operation in which the output rotation number is made variable, the brake 10 is released to thereby perform the same operation as in the case of the first example. In this case, the clutch 12 is made "on" . When the hydraulic pump 3 or hydraulic motor 6 has malfunctioned, or leakage of the pressure oil has occurred in the oil pipe 5 system, with the result that the adjustment of the rotation number of the ring gear 7 by the hydraulic motor 6 has become disabled, the brake 10 is made "on" to thereby make the ring gear 7 stationary. As a result, the ring gear 7 is made stationary, whereby the rotation of the input shaft 1 is made to have its rotation number decreased down to a fixed rotation number by the planetary gear 11 and carriers 9 and this speed reduced rotation thereof is transmitted to the output shaft 8. It is to be noted that during an operation in which the ring gear 7 has been made stationary due to the malfunction or the like of the hydraulic system, the clutch 12 is made "off" to thereby interrupt the transmission of the torque from the pump driving gear 2 to the hydraulic pump 3 and thereby stop the operation of the hydraulic system. Also, during a normal operation of the hydraulic system, when the rotation number of the input shaft 1 has changed and it is wanted to maintain the rotation number of the output shaft 8 to be at a fixed value, it is arranged to release the brake 10 and make the clutch 12 "on" to thereby adjust the rotation of the ring gear 7 and thereby rotate the output shaft 8 with a fixed number of rotations. In a third example to explain the present invention that is illustrated in Fig. 5, the variable amount of discharge type hydraulic pump 3 and the variable/reversible rotation type hydraulic motor 6 are provided close to each other, or are provided with their housings being coupled to each other and integrated. Further, an oil passage that replaces the oil pipe 5 (see Fig. 1) is provided within the pump 3 and motor 6. Further, it is arranged to input the torque to the hydraulic pump 3 from an input shaft 1a that is separate from the sun gear 4. In this example, the operation thereof is the same as that in the first example excepting that the torque to be input to the hydraulic pump 3 is made inputtable thereto from the independent input shaft 1a. And the amount of discharge of the hydraulic pump 3 is electrically or manually controlled. According to this example, since the hydraulic pump 3 and hydraulic motor 6 are structurally integrated with each other, the use of the hydraulic piping that is exposed to the outside becomes unnecessary. Further, the use of the hydraulic-pump driving gear system becomes also unnecessary. As a result, the entire structure of the apparatus becomes simplified and miniaturized. Also, since the input shaft 1a has been provided independently from the input shaft 1 of the epicycle reduction gear device 100, the rotation number of the hydraulic pump 3 becomes controllable irrelevantly to and independently of the epicycle reduction gear device 100. Therefore, when the rotation number of the input shaft 1 has changed and it is wanted to maintain the rotation number of the output shaft 8 to be at a fixed target rotation number, it is possible by adjusting the rotation number of the input shaft 1a of the hydraulic pump 3 to easily set the rotation number of the output shaft 8 to be at the target rotation number. In a fourth example that is illustrated in Fig. 6, a brake 10 that can brake the rotation of the ring gear 7 and that is similar to that which is illustrated in Fig. 3(A) or 3(B) is additionally provided on the variable speed power transmission apparatus according to the third example illustrated in Fig. 5. In the fourth example, during an ordinary variable speed operation, the brake 10 is released (made "off") and the rotation number of the input shaft 1a of the hydraulic pump 3 is changed to thereby perform the same operation as in the case of the third example illustrated in Fig. 5. When an inconvenience such as malfunction has occurred in the hydraulic system, the brake 10 is made "on" to thereby make the ring gear 7 stationary and thereby operate the output shaft 8 with a rotation number that has been decreased in a prescribed speed ratio from the rotation number of the input shaft 1. Also, even when no such inconvenience has occurred in the hydraulic system, in a case where the output shaft 8 is operated with the rotation number thereof being set to be fixed, the brake 10 is made "on" to thereby make the ring gear 7 stationary and thereby operate the output shaft 8 with a rotation number that has been decreased in a prescribed speed ratio from the rotation number of the input shaft 1. Further, when the rotation number of the input shaft 1 has changed and it is needed to maintain the rotation number of the output shaft 8 to be at a fixed value, the brake 10 is made "off" and the rotation number of the hydraulic-pump 3 side input shaft 1a is adjusted to thereby adjust the rotation number and rotation direction of the ring gear 7 and thereby maintain the rotation number of the output shaft 8 to be at a fixed value. In a first embodiment of the present invention that is illustrated in Fig. 7, a worm mechanism 200 composed of a worm 21 and a worm wheel 22 is interposed between the hydraulic motor 6 and the ring gear 7 of the epicycle reduction gear device 100 which are used in the first example illustrated in Fig. 1. That is, in Fig. 7, a reference numeral 21 denotes the worm that has been fixed to a worm shaft 61 that is connected directly to an output end of the hydraulic motor 6, a reference numeral 22 denotes a worm wheel that is meshed with the worm 21, a reference numeral 221 denotes a wheel shaft that has the worm wheel 22 fixed thereto, a reference numeral 141 denotes an input gear that is fixed to the wheel shaft and meshed with the ring gear, and a reference numeral 31 denotes a power source. The remaining construction is the same as in the case of the first embodiment illustrated in Fig. 1 and therefore the illustration thereof is made with the same members or components being denoted by the same reference symbols. In the first embodiment of the invention that is illustrated in Fig. 7, the torque that is transmitted from the power source 31 is transmitted from the input shaft 1 to the epicycle reduction gear device 100 while, on the other hand, the hydraulic pump 3 is driven through the input shaft gear 13 and then through the pump driving gear 2. The pressure oil that is supplied from the hydraulic pump 3 is supplied to the hydraulic motor 6 through the oil pipe 5, whereby the hydraulic motor 6 is driven by this pressure oil. The rotation of the hydraulic motor 6 has its speed reduced by the worm 21 and the worm wheel 22 and this speed reduced rotation is transmitted to the ring gear 7 through the input gear 141. The operation in which the ring gear 7 is forward rotated, reverse rotated or stopped by the control that is made of the rotation number of the hydraulic motor 6 is the same as in the case of the first example illustrated in Fig. 1. Also, when an overload has acted on the output shaft 8 side, this overload acts, through the epicycle reduction gear device 100, on the worm mechanism 200 composed of the worm 22 and the worm wheel 21. In consequence, the overload is undertaken by the worm mechanism 200 as a result of the reverse rotation prevention action that results from the mesh between the worm 22 and the worm wheel 21. In consequence, it is impossible that an excessive torque that results from this overload acts on the hydraulic motor 6 and its driving system. In a second embodiment that is illustrated in Fig. 8, the ring gear 7 of the epicycle reduction gear device 100 is connected to a hydraulic transmission that is driven by a power source. That is, in Fig. 8, a reference numeral 32 denotes a mechanical transmission, a reference numeral 31 denotes the power source and a reference numeral 33 denotes the hydraulic transmission. Whereby, the drive force of one driving system for driving the output shaft 310 of the power source 31 is transmitted to the input shaft 1 of the epicycle reduction gear device 100 through the mechanical transmission 32 while, on the other hand, the drive force of the other driving system that branches off from the output shaft 310 is transmitted to the hydraulic transmission 33 through gears 35 and 34. Also, the output end of the hydraulic transmission 33 is connected to the ring gear 7 through a gear 41. In the second embodiment, the rotation direction, rotation number, transmission torque, etc. of the hydraulic transmission 33 are controlled by a controller device not illustrated and, by the output torque that results from this control, the ring gear 7 is forward rotated, reverse rotated or stopped. On the other hand, because of the torque of the input shaft 1 being made changeable by the mechanical transmission 32, it results that the input shaft 1 and the ring gear 7 can be controlled respectively by the mechanical transmission 32 and the hydraulic transmission 33. This enables the operation of the variable speed power transmission apparatus over a wide range of rotation control. In a third embodiment of the present invention that is illustrated in Fig. 9, the worm mechanism 200 composed of the worm 21 and the worm wheel 23 that is the same as in the case of the first embodiment illustrated in Fig. 7 is interposed between the output end of the hydraulic transmission 33 and the ring gear 7. That is, in Fig. 9, the reference numeral 31 denotes the power source, the reference numeral 32 denotes the mechanical transmission, and the reference numeral 33 denotes the hydraulic transmission. Whereby, the hydraulic transmission 33 is driven by the drive force that has been made to branch off from the output shaft 310 through gears 35 and 34. And, to the output end of the hydraulic transmission 33, as in Fig. 7, there is connected the worm 21 of the worm mechanism 200 in interlocking relation with it. With this worm 21 there is meshed the worm wheel 22. Further, to this worm wheel 22 there is connected the ring gear 7 of the epicycle reduction gear device 100. By making this construction, when the rotation of the hydraulic transmission 33 is changed, the ring gear 7 is forward rotated, reverse rotated or stopped interlockingly therewith. In this third embodiment, when an overload acts on the output shaft 8 side, as in the case of the first embodiment illustrated in Fig. 7 this overload is undertaken by the worm mechanism 200. As a result of the reverse rotation prevention action of this worm mechanism 200, an excessive torque that results from this overload is prevented from being transmitted to the hydraulic transmission 33. It is to be noted that although in each of the above-mentioned embodiments the hydraulic motor or hydraulic transmission 33 has been connected to the ring gear 7, the present invention is not limited thereto. This system may be of any type if it is a reversible/variable rotation type hydraulic driver system that is driven by the oil pressure.

Claims: A variable speed power transmission apparatus comprising an epicycle reduction gear device (100) that has planetary gears (11) whose shafts are supported at equal intervals taken circumferentially thereof by carriers (9) fixed to an output shaft (8) thereof, the planetary gears (11) being meshed between external teeth of a sun gear (4) fixed to an input shaft (1) for receiving a torque from a drive source (31) and internal teeth of a ring gear (7), and a variable speed hydraulic driver system that is adapted to be driven by an oil pressure in such a way as to be variably and reversibly rotated by the oil pressure, an output shaft of the variable speed hydraulic driver system being connected to the ring gear (7) in interlocking relation therewith to thereby cause forward rotation, reverse rotation or stoppage of the ring gear (7) by the variable speed hydraulic driver system, wherein the variable speed hydraulic driver system comprises a variable amount of discharge type hydraulic pump (3) and a variable speed and reversible rotation type hydraulic motor (6) that is driven by a pressure oil supplied from the hydraulic pump (3), characterized in that an output shaft (61) of the hydraulic motor (6) has a worm (21) fixed thereto, the worm (21) being meshed with a worm wheel (22) that is connected to the ring gear (7), whereby the ring gear (7) is forward rotated, reverse rotated or stopped by the hydraulic motor (6). The variable speed power transmission apparatus as set forth in claim 1, characterized in that a transmission (32) is provided for inputting the torque from the drive source (31) to the input shaft (1), and a hydraulic transmission (33) is provided for receiving the torque from the drive source (31) through a transmission path (34,35) that branches off from a transmission path that leads to the transmission (32), an output shaft of the hydraulic transmission (33) being interlockingly connected to the worm (21). The variable speed power transmission apparatus as set forth in claim 1 or 2, characterized in that the ring gear has additionally provided thereon a brake for stopping the rotation thereof.

Inventors: ITO HIDEKI, KAWAKAMI SOICHI, SAITO HIROSHI, ITO, HIDEKI, KAWAKAMI, SOICHI, SAITO, HIROSHI, Ito, Hideki, Mitsubishi Heavy Industrie Ltd., Kawakami, Soichi, Mitsubishi Heavy Industrie Ltd., Saito, Hiroshi, Mitsubishi Heavy Industrie Ltd.
Applicants: MITSUBISHI HEAVY IND LTD, MITSUBISHI HEAVY INDUSTRIES, LTD.
Application year: 1997
Main classification: F16H47
IPC codes: F16H47, F16H3