HYDROMECHANICAL TRANSMISSION

Abstract: A hydromechanical transmission that can be used as a simple and efficient continuously variable transmission comprising a differential mechanism (4) for forming either a first high-speed mechanical transmission line (a) or a second low-­ speed mechanical transmission line (b), a hydraulic power transmission mechanism (8) comprising two hydraulic pump/motors (5, 7), one of said hydraulic pump/motors being of the fixed displacement type, and the other is of the variable displacement type, and a mode selection mechanism for selecting either a low-speed mode or a high-speed mode in function of that mechanical transmission line (a, b) connecting the output shaft (19) to the input shaft (13).

Description: The present invention relates to a hydromechanical transmission which can be used in various industrial fields as an efficient nonstep continuously variable transmission. A hydrostatic power transmission which uses a pair of hydraulic pump/motors (reversible hydraulic machines) and is employed as a continuously variable transmission is well-known in the art. Such a transmission presents the advantage of enabling the output speed to be continuously varied. However, where it is used to drive a device to be run at low torque and high speeds, such as a winder or a centrifugal separator, both the hydraulic pump/motors required to have a variable displacement in order to be efficient. A known hydrostatic power transmission used to drive such a device is shown in Fig. 3, where the hydraulic pump/motors p and q of the variable displacement type are connected in series with each other via a hydraulic circuit r. (A booster circuit and other circuits are not represented). Power from a prime mover is applied to one of the hydraulic pump/motor p, and the power delivered from the other pump/motor q can be transmitted to the rotor or a centrigufal separator, the driving wheels of an automobile, or the like. The transmission is controlled as shown in Fig. 4 up to a stationary operation at high-speed so as to improve the efficiency of the system as much as possible. More specifically, when the system is started, the displacement of the pump/motor q (on the output side) is set at its maximum value, while the displacement of the other pump/motor p (on the input side) is made zero. Then, the displacement of the pump/motor p acting as a pump on the input side is gradually increased. Thus, the hydraulic pump/motor q functioning as a motor on the output side increases its rotational speed while keeping providing a high torque. When the maximum displacement of the pump/­ motor p on the input side is attained, the control over the displacement of said pump/motor p is stopped. Then, the displacement of the pump/motor q on the output side is gradually reduced. Thus, the rotational speed of said pump/motor q on the output side is increased while the torque is simultaneously decreased until reaching a certain stationary high-­ speed. In other words, the transmission operates at constant torque and low speeds until the displacement of the pump/motor p (on the input side) attains its maximum value. Thereafter, the displacement of the pump/motor q (on the output side) is controlled, and the transmission is operated at constant power and high speeds. Therefore, the transmission can operate efficiently, taking full advantage of its characteristics. In general, hydraulic pump/motors of the variable displacement type have many movable parts which are complex in structure and must be precisely machined. Therefore, the structure of the whole transmission is complex and expensive to manufacture, more especially as two such hydraulic pump/motors must be used, and the displacements of the respective pump/motors must be separately controlled. Another disadvantage of the known system results from the fact that hydraulic pump/motors of the variable displacement type generally leak more working fluid than the pump/motors of the fixed displacement type, because they incorporate more sliding and/or rotating seals. Therefore, the variable-displacement type tends to exhibit slightly larger energy loss than the fixed-displacement type. This might adversely affect the efficiency of the whole system. It is the object of the present invention to provide a hydromechanical transmission completely free of the foregoing problems. This object is achieved by a hydromechanical transmission characterized in that it comprises : a differential mechanism having first, second, third input/output ends and forming either a first low-­ speed mechanical transmission line between the first and second input/output ends or a second high-speed mechanical transmission line between the first and third input/output ends ; a hydraulic power transmission mechanism comprising a pair of hydraulic pump/motors whose respective input/output shafts are connected to said second and third input/output ends, respectively, of said differential mechanism, said pump/motors cooperating with each other to constitute variable-­ speed hydraulic power transmission lines, one of said hydraulic pump/motors being of the fixed displacement type and the other pump/motor being of the variable displacement type ; and a mode selection mechanism for selecting either a low-speed mode, in which the output shaft of the hydromechanical transmission is connected to the input shaft via said first mechanical transmission line, or a high-speed mode, in which said output shaft is connected to the input shaft via said second mechanical transmission line. In the low-speed mode, the output is connected to the input through the first low-speed mechanical transmission line, said transmission line being formed between the first and second input/output ends of the differential mechanism. A portion of the power applied is delivered through this line. The remaining power is transmitted toward the output shaft via the hydraulic power transmission line formed by the hydraulic power transmission mechanism. In this case that of the pump/motors which acts as a pump is of the variable displacement type, and is varied from zero to its maximum value so that the other pump/motor functioning as a motor increases its rotational speed at a constant high torque. The output shaft of the hydromechanical transmission shows same characteristics. In the high-speed mode, the output is connected to the input via the second high-speed mechanical transmission line, said line being formed between the first and third input/output ends of the differential mechanism. A portion of the power applied is delivered through this line. The remaining power is transmitted toward the output shaft via the hydraulic power transmission line formed by the hydraulic power transmission mechanism. At this time, the roles of the pump/motors, i.e., functioning as a pump or as a motor, are interchanged. In other words, the pump/motor of the variable displacement type now acts as a pump. Therefore the displacement of the pump/motor of the variable displacement type is reduced from its maximum value toward zero in the manner opposite to the foregoing, so that said pump/­ motor increases its rotational speed. The output of the hydromechanical transmission shows same characteristics. Fig. 1 is a flow line diagram of a hydromechanical transmission according to the invention. Fig. 2 is a graph for illustrating the operation of the transmission shown in Fig. 1. Fig. 3 is a circuit diagram of a conventional hydrostatic transmission ; and Fig. 4 is a graph for illustrating the operation of the conventional transmission shown in Fig. 3. A hydromechanical transmission according to the invention is schematically shown in Fig. 1. The transmission comprises a differential mechanism 4, a hydraulic power transmission mechanism 8, and a mode selection mechanism 9. The differential mechanism 4 presents first, second, third input/­ output ends 1, 2, 3, respectively, and forms either a first low-speed mechanical transmission line a between the first input/output end 1 and the second input/output end 2 or a second mechanical transmission line b for high speeds between the first end 1 and the thrid end 3. A hydraulic pump/motor 5 of the fixed displacement type comprises an input/­ output end 5a connected to the second input/output end 2 of the differential mechanism 4. A hydraulic pump/motor 7 of the variable displacement type presents an input/output end 7a coupled to the third input/output end 3. The pump/motors 5 and 7 cooperate with each other to constitute variable-­ speed hydraulic transmission lines A and B. The mode selection mechanism 9 selects either a low-speed mode, in which the output is connected to the input via the first mechanical transmission line a, or a high-­ speed mode, in which the output is connected to the input via the second mechanical transmission line b. The differential mechanism 4 is a planetary gear train consisting of planetary gears 4a circumferentially regularly spaced apart from each other and a sun gear 4b. The planetary gears 4a are in mesh with an outer ring gear 4c. The planetary gears 4a are mounted in a gear carrier 4d. The first input/output end 1 is provided at the center of said carrier 4d, and extends in the form of the transmission input shaft 13. The sun gear 4b is supported on a pivot 4e, which is used as the second input/output end 2. A gear 14 is fixedly secured to said second end 2. The ring gear 4c has a boss 4f that is used as the third input/output end 3. A gear 15 is coupled to said third end 3. In the hydraulic power transmission mechanism 8, the pump/motor 5 of the fixed displacement type is connected in series with the pump/motor 7 of the variable displacement type via a hydraulic circuit 16, in the same way as in an ordinary hydrostatic power transmission. The input/output shaft 5a of the pump/­ motor 5 is coupled to the pivot 4e of sun gear 4b. The input/output shaft 7a of the pump/motor 7 is connected to the ring gear 4c by means of a pinion 17. The mode selection mechanism 9 has a low-speed clutch 21 inserted between a low-speed gear 18 and the output shaft 19 of the transmission. The gear 18 meshes with the gear 14 at the second input/output end 2. The mechanism 9 further comprises a high-speed clutch 23 inserted between a high-speed gear 22 and the output shaft 19, said gear engaging with gear 15 at the third input/output end 3. In this embodiment, rotary power from an electric motor or the like is applied to the input shaft 13 mounted at the first input/output end 1 of the differential mechanism 4. Then, rotary power is delivered from the output shaft 19 which is connected to the second input/output end 2 or the third input/output end 3 of the differential mechanism 4 via the mode selection mechanism 9. The power may then be transmitted for example to a take-up roller or the like. In the operation of the hydromechanical transmission constructed as described above, when the low-speed mode is selected, the low-speed clutch 21 is engaged but the high-speed clutch 23 is disengaged. Under the low-­ speed mode, the output is connected to the input through the low-speed mechanical transmission line a formed between the first end 1 and the second end 2 of the differential mechanism 4. Thus, a portion of the power applied is transmitted to the output shaft 19 via mechanical transmission line a. At this time, the pump/motor 7 of the variable displacement type functions as a pump, while the pump/motor 5 of the fixed displacement type acts as a motor. Accordingly, the rotary power appearing at the third end 3 of the differential mechanism 4 is transmitted to the output shaft 19 via the hydraulic transmission line A that is formed between the pump/motor 7 and the pump/motor 5. In the low-speed mode, as the displacement of the pump/motor 7 is increased, the rotational speed of the output shaft 19 increases relatively to the rotational speed of the input shaft 13. More specifically, when the displacement of the pump/motor 7 of the variable displacement type is zero, the third input/output end 3 of the differential mechanism 4 substantially runs idle. Therefore, the output shaft 19 connected to the second input/output end 2 of the differential mechanism 4 is substantially at a standstill. Then, as the displacement of the pump/motor 7 is increased, the rotational speed at the third end 3 decreases relatively, and the speed at the second end 2 increases relatively, and when the two speeds are equal, the clutch 21 of the mode selection mechanism 9 is disengaged, while the high-speed clutch 23 is engaged to select the high-speed mode. In the high-speed mode, the mechanical transmission line b is formed between the first end 1 and the third end 3 of the differential mechanism 4 and a portion of the power applied is transmitted to the output shaft 19 via this line b. At this time, the pump/motor 7 of the variable displacement type functions as a motor, while the pump/motor 5 of fixed displacement type acts as a pump. Thus, the rotary power appearing at the second end 2 of the differential mechanism 4 is transmitted to the output shaft 19 via the hydraulic transmission line B that is formed between the hydraulic pump/motor 5 and the hydraulic pump/motor 7. In the high-speed mode, as the displacement of the pump/motor 7 is reduced, the rotational speed of the output shaft 19 increases relative to the rotational speed of the input shaft 13. In other words, as the displacement of the pump/motor 7 is reduced, the speed at the third end 3 increases relatively, while the rotational speed at the second end 2 decreases relatively. Since the hydromechanical transmission is designed as described thus far, it is capable of providing accelerations with a high torque, in the low-speed mode. On the other hand, in the high-speed mode, it is able to run at high speeds and low torque. Moreover, in such a transmission, the roles of the pump/motors 5 and 7, forming a pair, are interchanged between the low-speed and high-speed modes. For this reason, constant-torque operation can be performed in the low-speed mode and constant-­ power operation can be effected in the high-speed mode, by means of the structure in which the displacement of pump/motor 7 is made variable, the displacement of the other pump/motor 5 being fixed. Consequently, the transmission requires a much less number of precisely machined parts than the transmission in which both hydraulic pump/motors have a variable displacement. Hence, the novel transmission is simpler in structure and less expensive to manufacture than the conventional transmission. In addition, the control system is simple in structure as well, since one needs only one two-position switch for the clutches 21 and 23 together with the control over the only variable displacement pump/motor 7. Finally, the energy loss which would have been caused by movable seals for varying displacement is halved. In this way, the efficiency of the whole system can be enhanced without introducing difficulties. Although the differential mechanism is not limited to a planetary gear train, the use of such a gear train facilitates making the system compact. Also in the embodiment, the differential mechanism is disposed on the input side to divide the input power. The invention is not limited to this structure. For example, it is also applicable to a structure where the output power is divided.

Claims: A hydromechanical transmission characterized in that it comprises : a differential mechanism (4) having first, second, third input/output ends (1, 2, 3) and forming either a first low-speed mechanical transmission line (a) between the first (1) and second (2) input/output ends or a second high-speed mechanical line (b) between the first (1) and third (3) input/output ends ; a hydraulic power transmission mechanism (8) comprising a pair of hydraulic pump/motors (5,7) whose respective input/output shafts (5a, 7a) are connected to said second (2) and third (3) input/­ output ends, respectively, of said differential mechanism (4), said pump/motors (5, 7) cooperating with each other to constitute variable-speed hydraulic power transmission lines (A, B), one (5) of said hydraulic pump/motors being of the fixed displacement type and the other pump/motor (7) being of the variable displacement type ; and a mode selection mechanism (9) for selecting either a low-speed mode, in which the output shaft (19) of the hydromechanical transmission is connected to the input shaft (13) via said first mechanical transmission line (a), or a high-speed mode, in which said output shaft (19) is connected to the input shaft (13) via said second mechanical transmission line (b).

Inventors: KITA, YASUO, SUGAWARA, RYOSUKE
Applicants: SHIMADZU CORPORATION
Application year: 1986
Main classification: F16H47
IPC codes: F16H47