WO2006126646A1 - 油圧駆動装置 - Google Patents
油圧駆動装置 Download PDFInfo
- Publication number
- WO2006126646A1 WO2006126646A1 PCT/JP2006/310476 JP2006310476W WO2006126646A1 WO 2006126646 A1 WO2006126646 A1 WO 2006126646A1 JP 2006310476 W JP2006310476 W JP 2006310476W WO 2006126646 A1 WO2006126646 A1 WO 2006126646A1
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- WO
- WIPO (PCT)
- Prior art keywords
- variable displacement
- hydraulic motor
- clutch
- displacement hydraulic
- shaft
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B23/00—Pumping installations or systems
- F04B23/04—Combinations of two or more pumps
- F04B23/06—Combinations of two or more pumps the pumps being all of reciprocating positive-displacement type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H39/00—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution
- F16H2039/005—Rotary fluid gearing using pumps and motors of the volumetric type, i.e. passing a predetermined volume of fluid per revolution comprising arrangements or layout to change the capacity of the motor or pump by moving the hydraulic chamber of the motor or pump
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/02—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type
- F16H2047/025—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the fluid gearing comprising a plurality of pumps or motors
Definitions
- the present invention relates to a hydraulic drive device provided in a construction machine having a traveling function such as a wheel loader.
- FIG. 5 is a skeleton diagram of a conventional hydraulic drive device
- FIG. 6 is a cross-sectional view showing a clutch portion provided in a second variable displacement hydraulic motor of the conventional hydraulic drive device.
- a first variable displacement hydraulic motor 8 which is a high speed low torque motor is connected to the final output shaft 2 via an output shaft 5, a gear 4 and a gear 3.
- the second variable displacement hydraulic motor 11 which is a low speed high torque motor, is connected to the final output shaft 2 via the output shaft 26, the clutch unit 10, the gear 6, the gear 4 and the gear 3.
- the clutch unit 10 is provided on the outer side of the output shaft 26 of the second variable displacement hydraulic motor 11 and rotates integrally with the output shaft 26.
- a drum 21 which can be rotated integrally with the clutch driving shaft 25 when the plate 21 is accommodated and the friction plates 21 abut each other, a clutch driven shaft 7 which can be rotated integrally with the drum 20, and a friction plate
- a piston 19 which makes 21 attachable and detachable, and a spring 12 which biases the piston 19 so that the friction plates 21 abut each other.
- each of the first variable displacement hydraulic motor 8 and the second variable displacement hydraulic motor 11 described above is a cylinder as generally considered in the technical field.
- a rotary member including a block and a plurality of pistons slidably accommodated in the cylinder block, output shafts 5, 26 integrally rotating with the rotary member, and a first for supplying and discharging oil. It has a valve plate having a port and a second port. That is, the first variable volume oil
- a rotary member related to the first variable displacement hydraulic motor 8, an output shaft 5, and a valve plate are provided in a front casing and a rear casing which form a main body of the pressure motor 8.
- the rotating member associated with the second variable displacement hydraulic motor 11, an output shaft 26, and a valve plate are provided in a front casing and a rear casing that form the main body.
- Patent Document 1 Japanese Patent Application Laid-Open No. 2000-193065
- the prior art described above has the front casing and the rear casing in which the first variable displacement hydraulic motor 8 and the second variable displacement hydraulic motor 11 respectively form the main body, the number of parts is increased and the manufacturing cost is increased. It is easy to get high. Also, each of the first variable displacement hydraulic motor 8 and the second variable displacement hydraulic motor 11 is disposed at a distance from each other. In addition, the size of the device has been increased. Furthermore, the piping associated with each hydraulic motor 8, 11 is required, and this piping structure tends to be complicated.
- the present invention is also achieved by the actual condition in the above-mentioned prior art, and the object is to reduce the number of parts and to make the first variable displacement hydraulic motor and the second variable displacement hydraulic motor close to each other. It is an object of the present invention to provide a hydraulic drive which can be arranged.
- the present invention provides a rotary member including a cylinder block and a piston, an output shaft that rotates integrally with the rotary member, a first port for supplying and discharging oil, and A first variable displacement hydraulic motor and a second variable displacement hydraulic motor each having a valve plate having a second port, an output of the first variable displacement hydraulic motor, and an output of the second variable displacement hydraulic motor are transmitted.
- a hydraulic drive capable of outputting from one final output shaft through one means, the rotary member of the first variable displacement hydraulic motor, a part of the output shaft, and the second variable displacement hydraulic motor
- a front casing which is a single member housing the rotary member and a part of the output shaft, and a front casing which is joined to the front casing, the valve plate of the first variable displacement hydraulic motor, and the second of the first variable displacement hydraulic motor; Variable volume And a rear casing on which the valve plate of the hydraulic motor is mounted.
- the present invention thus configured can The number of rear casings can be reduced. That is, the number of parts can be reduced.
- first variable displacement hydraulic motor and the second variable displacement hydraulic motor are disposed in one set of the front casing and the rear casing, these first variable displacement hydraulic motor and the second variable displacement motor are arranged.
- the displacement hydraulic motors can be arranged in close proximity to one another.
- the rear casing includes an oil passage communicating with the first port of the valve plate of the first variable displacement hydraulic motor, and the oil passage communicating with the oil passage.
- the thus configured present invention can form, as an oil passage, in the rear casing, a pipe for guiding oil supplied to and discharged from the first variable displacement hydraulic motor and the second variable displacement hydraulic motor.
- the present invention is characterized in that, in the above invention, an oil passage for supplying oil in an oil chamber formed in the front casing to the transmission means is provided.
- the present invention thus configured can effectively utilize the oil in the oil chamber formed in the front casing for the lubrication of the transmission means.
- the present invention is characterized in that, in the above-mentioned invention, the oil passage for supplying the oil in the oil chamber to the transmission means is provided in the front casing.
- the thus configured present invention can realize the lubrication of the transmission means with a simple structure.
- the present invention is characterized in that, in the above-mentioned invention, the transmission means includes a clutch portion provided on an output shaft of the second variable displacement hydraulic motor.
- a clutch driving shaft in which the clutch unit rotates integrally with an output shaft of the second variable displacement hydraulic motor, and a clutch driving shaft can be brought into contact with or separated from the clutch driving shaft.
- a clutch driven shaft for transmitting the output of the second variable displacement hydraulic motor to the final output shaft at the time of connection, and including the output shaft of the second variable displacement hydraulic motor and the clutch driving shaft of the clutch portion.
- one end of the clutch driving shaft is the second variable displacement motor because the clutch driving shaft included in the clutch portion has the same member force as the output shaft of the second variable displacement motor.
- the bearing for supporting the other end of the clutch drive shaft which does not need to be provided with a bearing for supporting the clutch drive shaft, can realize the support structure of the clutch drive shaft. That is, the bearing supporting the clutch drive shaft may be provided only in association with the other end of the clutch drive shaft, whereby the number of bearings can be reduced.
- the clutch driven shaft of the clutch unit is disposed coaxially with the clutch driving shaft on the clutch driving shaft portion of the clutch unit.
- the shaft length of the driven shaft is set shorter than the shaft length of the clutch drive shaft It is characterized by
- the present invention configured in this manner can increase the axial length of the output shaft of the second variable displacement motor and the clutch driving shaft. By relatively shortening the shaft length, it is possible to set the entire length dimension along the axial direction of the output shaft of the second variable displacement motor short.
- a drum which rotates integrally with the clutch driving shaft of the clutch portion, and in this drum, a friction plate for separating the drum and the clutch driven shaft from each other
- a piston is provided which can drive the friction plate so as to connect the drum and the clutch driven shaft, and a spring which biases the piston.
- the present invention is characterized in that, in the above-mentioned invention, the transmission means includes a clutch portion provided on an output shaft of the first variable displacement hydraulic motor.
- a clutch driving shaft in which the clutch unit rotates integrally with an output shaft of the first variable displacement hydraulic motor, and a clutch driving shaft can be brought into contact with or separated from it. And a clutch driven shaft for transmitting the output of the second variable displacement hydraulic motor to the final output shaft when connected.
- a gear is provided, which rotates integrally with the clutch driven shaft and transmits rotation of the output shaft of the second variable displacement hydraulic motor to the clutch driven shaft.
- the clutch driven shaft is not influenced by the rotation of the first variable displacement hydraulic motor when the clutch portion is disengaged, whereby the clutch driving shaft and the clutch driven shaft can be obtained.
- the relative rotational speed can be suppressed to less than or equal to the rotational speed of the output shaft of the first variable displacement hydraulic motor.
- a transmission including an oil chamber of a motor portion including the front casing and the rear casing, and a transmission case continuously provided to the motor portion in an upper portion of the front casing.
- a transmission case continuously provided to the motor portion in an upper portion of the front casing.
- the lower part of the mission case is provided with an oil passage that defines the height of the oil level of the oil accommodated in the mission case.
- the oil passage provided in the upper portion of the front casing is used.
- the oil in the oil chamber of the motor unit can be supplied to lubricate parts in the transmission case, and the oil passage provided in the lower part of the transmission case allows the amount of oil contained in the transmission case to be reduced. It can be held to the minimum necessary.
- the present invention is characterized in that, in the above-mentioned invention, a parking brake capable of braking the output shaft of the first variable displacement motor is provided.
- the first variable displacement hydraulic motor and the second variable displacement hydraulic motor are disposed in one set of the front casing and the rear casing, the number of parts can be reduced. Compared to the manufacturing cost can be reduced. Further, the first variable displacement hydraulic motor and the second variable displacement hydraulic motor can be disposed close to each other, whereby the device can be miniaturized.
- the pipes for guiding the oil supplied to and discharged from the first variable displacement hydraulic motor and the second variable displacement hydraulic motor can be formed as an oil passage in the rear casing, this piping structure can be simplified as compared with the prior art. can do.
- FIG. 1 is a cross-sectional view showing a first embodiment of a hydraulic drive system according to the present invention
- FIG. 2 is a skeleton diagram of the first embodiment shown in FIG.
- a construction machine etc. for example, a wheel loader
- a first variable displacement hydraulic motor 30 forming a high speed low torque motor
- a second variable displacement oil pressure forming a low speed high torque motor
- a motor 31 is provided.
- the output of the first variable displacement hydraulic motor 30 and the output of the second variable displacement hydraulic motor 31 can be output from one final output shaft 41 via transmission means, that is, gears 35, 39, 40 and a clutch part 34. It has become.
- a clutch unit 34 capable of transmitting the output of the second variable displacement hydraulic motor 31 to the final output shaft 41 is provided on the output shaft 32 of the second variable displacement hydraulic motor 31 and is rotated integrally with the output shaft 32. Including a clutch driving shaft 34a that rotates, and a clutch driven shaft 34e that is provided so as to be able to contact with or separate from the clutch driving shaft 34a and that transmits the output of the second variable displacement hydraulic motor 31 to the final output shaft 41 when connected.
- the output shaft 32 of the second variable displacement hydraulic motor 31 and the clutch driving shaft 34a of the clutch portion 34 are made of the same member. That is, the second variable A clutch driving shaft 34 a of the clutch portion 34 is formed on an extension of the output shaft 32 of the displacement hydraulic motor 31.
- the clutch driven shaft 34e of the clutch portion 34 described above is disposed coaxially with the clutch driven shaft 34a at the portion of the clutch driven shaft 34a.
- the axial length is set shorter than the axial length of the clutch drive shaft 34a.
- the clutch driven shaft 34 e is engaged with the gear 35. That is, the clutch driven shaft 34e and the gear 35 are integrally rotated.
- the gear 35 is supported by a bearing 35a so that the clutch drive shaft 34a and the gear 35 do not rotate as a unit between the clutch drive shaft 34a and the gear 35.
- the clutch portion 34 includes a drum 34b provided integrally with the clutch driving shaft 34a, ie, integrally rotating with the clutch driving shaft 34a, in addition to the clutch driving shaft 34a and the clutch driven shaft 34e.
- a friction plate for example, a fixed friction plate 34g fixed to the clutch driven shaft 34e, a movable friction plate 34f capable of coming into contact with the fixed friction plate 34g, and the movable friction plate 34f are fixed.
- a piston 34c that can be pressed to 34g and a spring 34d that biases the movable friction plate 34f away from the fixed friction plate 34g are disposed.
- An oil passage 34h is connected to the clutch driving shaft 34a and the drum 34b to guide the oil pressure for driving the piston 34c so that the movable friction plate 34f abuts against the fixed friction plate 34g by being piled by the spring force of the spring 34d. , 34i are formed.
- one end of the clutch driving shaft 34 a is integrated with the output shaft 32 of the second variable displacement hydraulic motor 31, and the other end is supported by the bearing 33.
- the first embodiment is provided with a parking brake 38 capable of braking the output shaft 36 of the first variable displacement hydraulic motor 30.
- the parking brake 38 is in contact with a housing 38a held in a fixed state, a friction plate disposed in the housing 38a, for example, a fixed friction plate 38e fixed to the housing 38a, and the fixed friction plate 38e.
- Possible movable friction plate 38d Possible movable friction plate 38d.
- the movable friction plate 38d is provided with a piston 38b capable of pressing the fixed friction plate 38e against the fixed friction plate 38e, and a spring 38c biasing the piston 38b such that the movable friction plate 38d is separated from the fixed friction plate 38e.
- the output shaft 36 of the first variable displacement hydraulic motor 30, and the housing 38a are provided with springs 38c. Oil passages 38f and 38g for guiding the hydraulic pressure for driving the piston 38b so as to abut the movable friction plate 38d in contact with the fixed friction plate 38e are formed.
- the gear 39 which fits into the gear 35 described above, is fixed to the output shaft 36 of the first variable displacement hydraulic motor 30.
- a gear 40 that fits into the gear 39 is fixed to the final output shaft 41.
- the end of the output shaft 36 of the first variable displacement hydraulic motor 30 is supported by a bearing 37.
- the front casing 50 is also provided.
- the rear casing 51 is provided with the front casing 50 and the valve plate 30C of the first variable displacement hydraulic motor 30 and the valve plate 31C of the second variable displacement hydraulic motor 31.
- the rear casing 51 is provided with an oil passage 52 communicating with the first port 30C1 of the valve plate 30C of the first variable displacement hydraulic motor 30, and a valve plate 31C communicating with the oil passage 52 with the second variable displacement hydraulic motor 31.
- Oil passage 53 communicating with the first port 31C1 of the first variable displacement valve, an oil passage 54 communicating with the second port 30C2 of the valve plate 30C of the first variable displacement hydraulic motor 30, and a second variable displacement hydraulic And an oil passage 55 communicating with the second port 31C2 of the valve plate 31C of the motor 31.
- the oil of the oil chamber 56 formed in the front casing 50 is supplied to the gears 35, 39, 40 included in the transmission means, for example, in the front casing 50. Oil path It has 50A.
- oil passages 52, 53, the first port 30C1 of the valve plate 30 and the first port 31C1 of the valve plate 31C are supplied, and the second port 30C2 of the valve plate 30C and the second of the valve plate 31C
- the pistons 30B and 31B are driven by the oil pressure discharged to the oil passages 54 and 55 through the 2 port 31C2, and the cylinder blocks 30A and 31A are rotated to output the torque integrally with the cylinder blocks 30A and 31A.
- Shafts 36 and 32 rotate.
- the clutch driving shaft 34 a rotates integrally with the rotation of the output shaft 32 of the second variable displacement hydraulic motor 31, and this rotation rotates the drum 34 b, the movable friction plate 34 f and the fixed friction plate 34 g, and the clutch driven shaft 34 e
- the rotation of the gear 35 is transmitted to the final output shaft 41 via the gears 39 and 40.
- the torque is transmitted to the final output shaft 41 via the torque gears 39, 40 of the output shaft 36 of the first variable displacement hydraulic motor 30. That is, the output of the second variable displacement hydraulic motor 31 and the output of the first variable displacement hydraulic motor 30 are transmitted to the final output shaft 41, whereby various operations at low speed traveling can be performed.
- the braking of the output shaft 36 of the first variable displacement hydraulic motor 30 by the parking brake 38 is released, and the displacement of the second variable displacement hydraulic motor 31 is set to 0, and the clutch portion 34 is disconnected. That is, except for the hydraulic force applied to the piston 34c through the oil passages 34h and 34i shown in FIG. 1, the piston 34c is moved so that the movable friction plate 34f is released from the fixed friction plate 34g by the force of the spring 34d.
- the transmission of the rotational force between the clutch driving shaft 34a and the clutch driven shaft 34e is shut off, for example, the oil passages 52 and 53, the first port 30C1 of the valve plate 30C, and the hydraulic fluid to the first port 31C1 of the valve plate 31C.
- the piston 30B of the first variable displacement hydraulic motor 30 is driven to rotate the rotary shaft 36 integrally with the cylinder block 30A and the cylinder block 30A, and via the second port 30C2 of the valve plate 30C. Hydraulic fluid is discharged to the oil passage 54.
- the second variable displacement hydraulic motor 31 which has a capacitive force ⁇ , the supply and discharge of hydraulic fluid is blocked, the piston 31B is not driven, and the cylinder block 31A does not rotate. Therefore, the working oil is supplied only to the first variable displacement hydraulic motor 30, and the rotation of the output shaft 36 of the first variable displacement hydraulic motor 30 is transmitted to the final output shaft 41 without loss via the gears 39 and 40. Therefore, high speed driving can be realized.
- the piston 38b is supplied with oil pressure through oil passages 38f and 38g shown in FIG. 1, and is piled by the force of the spring 38c so that the movable friction plate 38d abuts against the fixed friction plate 38e.
- the rotation of the output shaft 36 of the first variable displacement hydraulic motor 30 is blocked, the rotation of the final output shaft 41 is stopped, and the vehicle is in the parking state.
- the clutch driving shaft 34a included in the clutch portion 34 is also the same member as the output shaft 32 of the second variable displacement hydraulic motor 31, the clutch driving shaft 34a One end is integrated with the output shaft 32 of the second variable displacement hydraulic motor 31.
- the bearing 33 supporting the other end of the clutch driving shaft 34a does not need to be provided with a bearing for supporting the clutch driving shaft 34a.
- the bearing 33 for supporting the clutch driving shaft 34a may be provided in association with only one end of the clutch driving shaft 34a, which is one end of the clutch driving shaft 34a. It can be reduced and the production cost can be reduced.
- the clutch driven shaft 34e is disposed coaxially with the clutch driving shaft 34a at a portion of the clutch driving shaft 34a, and the axial length of the clutch driven shaft 34e is shorter than the axial length of the clutch driving shaft 34a.
- the output shaft of the second variable displacement hydraulic motor 31 can be obtained by relatively shortening the axial length of the output shaft 32 of the second variable displacement hydraulic motor 31 and the axial length of the clutch driving shaft 34a.
- the overall length dimension along 32 can be set short, and the device can be miniaturized.
- the parking brake 38 capable of braking the output shaft 36 of the first variable displacement hydraulic motor 30 is provided, the torque required for braking can be small, and the parking brake 38 can be made compact. .
- first variable displacement hydraulic motor 30 and the second variable displacement hydraulic motor 31 are disposed inside one set of the front casing 50 and the rear casing 51, the front casing 50 and the rear casing are provided.
- the number of 51 can be reduced. That is, the number of parts can be reduced, which can reduce the manufacturing cost.
- first variable displacement hydraulic motor 30 and the second variable displacement hydraulic motor 31 are disposed in the inside of one pair of front casing 50 and rear casing 51, these first variable displacement hydraulic motors 31 and The motor 30 and the second variable displacement hydraulic motor 31 can be arranged close to each other, which makes it possible to miniaturize the device.
- the piping for guiding the oil supplied to and discharged from the first variable displacement hydraulic motor 30 and the second variable displacement motor 31 can be formed as the oil passages 52 to 55 in the rear casing 51, so this piping structure Can be simplified.
- the oil passage 50A for supplying the oil of the oil chamber 56 formed in the front casing 50 to the gears 35, 39, 40 included in the transmission means is provided, the oil chamber of the front casing 50 is provided. 5 6 oil can be effectively used to lubricate gears 35, 39 and 40.
- the oil passage 50A is provided in the front casing 50, lubrication of the gears 35, 39, 40 can be realized with a simple structure.
- FIG. 3 is a cross-sectional view showing a second embodiment of the hydraulic drive system according to the present invention
- FIG. 4 is a skeleton diagram of the second embodiment shown in FIG.
- This second embodiment is also provided in, for example, a wheel loader, and takes into consideration the actual arrangement of the wheel loader.
- FIGS. 3 and 4 is the same as the one shown in FIGS. 1 and 2 described above. Is drawn. That is, the part drawn on the upper side of FIGS. 3 and 4 is a part that is preferably arranged on the upper side when provided in the wheel loader, and the part drawn on the lower side of FIGS. , It is preferable to be placed on the lower side U, a part.
- the motor unit 60 including the front casing 50 and the rear casing 51 and the transmission unit 61 including the transmission case 63 are connected in a row.
- a front casing 50 accommodates a cylinder block 31A constituting a member, a plurality of pistons 31B, and a part of the output shaft 32 of the first variable displacement hydraulic motor 31.
- valve plate 30 C of the first variable displacement hydraulic motor 30 and the valve plate 31 C of the second variable displacement hydraulic motor 31 are accommodated in the rear casing 51.
- the rear casing 51 communicates with an oil passage 52 communicating with the first port 30C1 of the valve plate 30C of the first variable displacement hydraulic motor 30, and with the oil passage 52.
- An oil passage 53 communicating with the first port 31C of the valve plate 31C of the second variable displacement hydraulic motor 31, an oil passage 54 communicating with the second port 30C2 of the valve plate 30C of the first variable displacement hydraulic motor 30, It communicates with oil passage 54 and the second variable displacement
- An oil passage 55 communicating with the second port 31C2 of the valve plate 31C of the hydraulic motor 31 is formed.
- the clutch portion 34 described above is fixed to the output shaft 36 of the first variable displacement hydraulic motor 30, and is provided so as to be in contact with the clutch driving shaft 34a that rotates integrally with the output shaft 36 and the clutch driving shaft 34a. And a clutch driven shaft 34e for transmitting the output of the second variable displacement hydraulic motor 31 to the final output shaft 41 via the friction plate 34fg at the time of connection.
- the transmission means for transmitting the output of the second variable displacement hydraulic motor 31 to the final output shaft 41 is provided with a gear 34el that rotates integrally with the clutch driven shaft 34e.
- a bearing is provided between the gear 34el and the output shaft 36 of the first variable displacement hydraulic motor 30, and the bearing does not transmit the rotation of the output shaft 36 of the first variable displacement hydraulic motor 30 to the gear 34el. It is supposed to be.
- the gear 35 fixed to the output shaft 32 of the second variable displacement hydraulic motor 31 and the gear 34el that rotates integrally with the above-mentioned clutch driven shaft 34e are in contact with each other, for example, the first variable displacement hydraulic pressure.
- These gears 35, 34el, 39, 40 are disposed so that the gear 39 fixed to the output shaft 36 of the motor 30 and the gear 40 fixed to the final output shaft 41 are in close agreement.
- the output of the first variable displacement hydraulic motor 30 and the output of the second variable displacement hydraulic motor 31 are transmitted to one final output shaft 41 by the gears 35, 34el, 39, 40 and the clutch part 34.
- the means of transmission are configured and spoken.
- An oil passage 66 communicating with the space 64 of the transmission portion 61 including the 63 is provided, and an oil passage 68 defining the height of the oil surface 67 of the oil accommodated in the transmission case 63 is provided at the lower portion of the transmission case 63. Is provided.
- the output shaft 36 of the first variable displacement hydraulic motor 30 and the second variable displacement hydraulic motor 31 are provided in the boundary wall separating the oil chamber 62 of the front casing 50 and the space 64 of the transmission case 63.
- Oil seals 65 are provided to seal around the output shaft 32 respectively.
- oil passages 69 are formed to introduce oil for lubricating the clutch portion 34, respectively.
- the output shaft 32 of the second variable displacement hydraulic motor 31 is The rotation of the first variable displacement hydraulic motor 30 is transmitted to the output shaft 36 of the first variable displacement hydraulic motor 30 via the gears 35 and 34el, the clutch driven shaft 34e, and the clutch driving shaft 34a, and the output shaft 36 of the first variable displacement hydraulic motor 30.
- the rotation is transmitted to the final output shaft 41 via gears 39, 40. That is, the output of the second variable displacement hydraulic motor 31 and the output of the first variable displacement hydraulic motor 30 are transmitted to the final output shaft 41. In this way, it is possible to carry out various operations by low speed traveling.
- the first variable displacement hydraulic motor 30 and the second variable displacement hydraulic motor 30 are disposed in the inside of the front case 50 and the rear casing 51 in a pair. Since the variable displacement hydraulic motor 31 is disposed, the number of front casings 50 and rear casings 51 can be reduced. That is, the number of parts can be reduced, which can reduce the manufacturing cost. In addition, since the first variable displacement hydraulic motor 30 and the second variable displacement hydraulic motor 31 are disposed in one set of the front casing 50 and the rear casing 51, these first variable displacement hydraulic motors are arranged. 30 and the second variable displacement hydraulic motor 31 can be arranged close to each other, which makes it possible to miniaturize the device.
- the pipes for guiding the oil supplied to and discharged from the first variable displacement hydraulic motor 30 and the second variable displacement motor 31 can be formed as the oil passages 52 to 55 in the rear casing 51, this piping structure can be simplified.
- the first variable displacement hydraulic motor 30 is provided with the clutch unit 34 capable of transmitting the output of the second variable displacement hydraulic motor 31 to the final output shaft 41, and Since the output of the first variable displacement hydraulic motor 30 and the output of the second variable displacement hydraulic motor 31 can be transmitted to the final output shaft 41 through the gear 39 fixed to the output shaft 36 of the motor 30, the clutch When the section 34 is shut off, the clutch driven shaft 34e of the clutch section 34 rotates the output shaft 36 of the first variable displacement hydraulic motor 30, that is, the rotation of the gear 39 fixed to the output shaft 36 of the first variable displacement hydraulic motor 30.
- the rotation speed of the clutch drive shaft 34a of the clutch unit 34 and the rotation speed of the clutch driven shaft 34e are not affected by the rotation of the gear 40 of the final output shaft 41 which is in mesh with the gear 39. It is necessary to suppress the significant increase of the relative rotational speed which is the difference. Kill. That is, the above-mentioned relative rotation number can be kept equal to or less than the rotation number of the output shaft 36 of the first variable displacement hydraulic motor 30.
- the oil in the oil chamber 62 of the front casing 50 can be supplied to the transmission case 63 through the oil passage 66 formed in the upper portion of the front casing 50, so that the transmission case 63 can be Good lubrication of gears 35, 34el, 39, 40, etc. can be realized. Furthermore, in this case, since the oil passage 68 defining the height of the oil surface 67 of the oil in the transmission case 63 is provided in the lower part of the transmission case 63, the amount of oil contained in the transmission case 63 Can be kept to the minimum required. As a result, the amount of oil in contact with the gear 40 and the like can be reduced, and torque loss and heat generation of oil due to the stirring resistance of the gear 40 and the like can be suppressed. Accordingly, damage to the clutch portion 34, the first variable displacement hydraulic motor 30, the second variable displacement hydraulic motor 31, and the like can be suppressed.
- the device can be realized with high durability and high reliability.
- the clutch portion 34 When the clutch portion 34 is disengaged, the clutch driven shaft 34e, the gear 34el that rotates integrally with the clutch driven shaft 34e, and the gear 35 fixed to the output shaft 32 of the second variable displacement hydraulic motor 31 are Since the rotation can be stopped, unnecessary torque loss can be reduced. This also contributes to the improvement of the durability and the realization of a highly reliable device.
- the gear 39 is fixed to the output shaft 36 of the first variable displacement hydraulic motor 30, but instead of this configuration, the gear 39 is used as a clutch drive shaft 34a You may make it the structure provided integrally.
- FIG. 1 is a cross-sectional view showing a first embodiment of a hydraulic drive system according to the present invention.
- FIG. 2 is a skeleton diagram of the first embodiment shown in FIG.
- FIG. 3 is a cross-sectional view showing a second embodiment of the hydraulic drive system according to the present invention.
- FIG. 4 is a skeleton diagram of the second embodiment shown in FIG.
- FIG. 5 is a skeleton diagram of a conventional hydraulic drive system.
- FIG. 6 is a cross-sectional view showing a clutch portion provided in a second variable displacement hydraulic motor of the conventional hydraulic drive system.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Motor Power Transmission Devices (AREA)
- Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
- Hydraulic Motors (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US11/915,041 US20090090103A1 (en) | 2005-05-26 | 2006-05-25 | Hydraulic Drive Device |
JP2007517898A JPWO2006126646A1 (ja) | 2005-05-26 | 2006-05-25 | 油圧駆動装置 |
EP06746855A EP1887253A4 (en) | 2005-05-26 | 2006-05-25 | HYDRAULIC DRIVE DEVICE |
Applications Claiming Priority (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2005-154168 | 2005-05-26 | ||
JP2005154161 | 2005-05-26 | ||
JP2005154168 | 2005-05-26 | ||
JP2005-154161 | 2005-05-26 |
Publications (1)
Publication Number | Publication Date |
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WO2006126646A1 true WO2006126646A1 (ja) | 2006-11-30 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2006/310476 WO2006126646A1 (ja) | 2005-05-26 | 2006-05-25 | 油圧駆動装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20090090103A1 (ja) |
EP (1) | EP1887253A4 (ja) |
JP (1) | JPWO2006126646A1 (ja) |
KR (1) | KR20080011393A (ja) |
WO (1) | WO2006126646A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2012008438A1 (ja) | 2010-07-14 | 2012-01-19 | 日立建機株式会社 | 動力伝達装置 |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010063084B3 (de) * | 2010-12-14 | 2012-04-12 | Sauer-Danfoss Gmbh & Co Ohg | Antriebsstrang eines Hydraulikantriebs mit einer Kupplung |
ITBS20130161A1 (it) * | 2013-11-08 | 2015-05-09 | Omsi Trasmissioni S P A | Gruppo di trasmissione per macchine industriali |
Citations (7)
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JPS5115224Y2 (ja) * | 1972-03-31 | 1976-04-22 | ||
JPS5944537B2 (ja) * | 1977-08-24 | 1984-10-30 | アイシン精機株式会社 | 自動車の無段変速機の速度比自動制御装置 |
JPH061906U (ja) * | 1992-06-10 | 1994-01-14 | 株式会社クボタ | 車両用ミッションギヤの潤滑装置 |
JPH0752666A (ja) * | 1993-08-10 | 1995-02-28 | Kanzaki Kokyukoki Mfg Co Ltd | 油圧トランスミッション |
US5518461A (en) * | 1993-03-08 | 1996-05-21 | Mannesmann Aktiengesellschaft | Dual hydraulic motor drive system |
JPH11141650A (ja) * | 1997-11-05 | 1999-05-25 | Mazda Motor Corp | 動力伝達装置 |
JP2000219056A (ja) * | 1999-01-29 | 2000-08-08 | Yanmar Diesel Engine Co Ltd | 油圧式無段変速機 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
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US3123975A (en) * | 1964-03-10 | Ebert | ||
GB1062874A (en) * | 1963-08-29 | 1967-03-22 | Dowty Technical Dev Ltd | Hydraulic apparatus |
GB1064651A (en) * | 1964-06-04 | 1967-04-05 | Dowty Technical Dev Ltd | Hydraulic power transmission apparatus |
JPS4824171B1 (ja) * | 1969-03-27 | 1973-07-19 | ||
DE19649195C1 (de) * | 1996-11-27 | 1998-01-08 | Brueninghaus Hydromatik Gmbh | Axialkolbenmaschine mit Lagerspülung |
DE19858958B4 (de) * | 1997-12-12 | 2006-08-17 | Komatsu Ltd. | Vorrichtung zur Steuerung mehrerer ölhydraulischer Motoren sowie einer Kupplung |
JP2004011769A (ja) * | 2002-06-06 | 2004-01-15 | Kubota Corp | 静油圧式無段変速装置 |
JP4101083B2 (ja) * | 2003-02-25 | 2008-06-11 | 株式会社クボタ | 作業車の走行変速制御装置 |
-
2006
- 2006-05-25 EP EP06746855A patent/EP1887253A4/en not_active Withdrawn
- 2006-05-25 WO PCT/JP2006/310476 patent/WO2006126646A1/ja active Application Filing
- 2006-05-25 JP JP2007517898A patent/JPWO2006126646A1/ja not_active Withdrawn
- 2006-05-25 US US11/915,041 patent/US20090090103A1/en not_active Abandoned
- 2006-05-25 KR KR1020077026685A patent/KR20080011393A/ko not_active Application Discontinuation
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5115224Y2 (ja) * | 1972-03-31 | 1976-04-22 | ||
JPS5944537B2 (ja) * | 1977-08-24 | 1984-10-30 | アイシン精機株式会社 | 自動車の無段変速機の速度比自動制御装置 |
JPH061906U (ja) * | 1992-06-10 | 1994-01-14 | 株式会社クボタ | 車両用ミッションギヤの潤滑装置 |
US5518461A (en) * | 1993-03-08 | 1996-05-21 | Mannesmann Aktiengesellschaft | Dual hydraulic motor drive system |
JPH0752666A (ja) * | 1993-08-10 | 1995-02-28 | Kanzaki Kokyukoki Mfg Co Ltd | 油圧トランスミッション |
JPH11141650A (ja) * | 1997-11-05 | 1999-05-25 | Mazda Motor Corp | 動力伝達装置 |
JP2000219056A (ja) * | 1999-01-29 | 2000-08-08 | Yanmar Diesel Engine Co Ltd | 油圧式無段変速機 |
Non-Patent Citations (1)
Title |
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See also references of EP1887253A4 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2012008438A1 (ja) | 2010-07-14 | 2012-01-19 | 日立建機株式会社 | 動力伝達装置 |
JPWO2012008438A1 (ja) * | 2010-07-14 | 2013-09-09 | 日立建機株式会社 | 動力伝達装置 |
Also Published As
Publication number | Publication date |
---|---|
EP1887253A1 (en) | 2008-02-13 |
KR20080011393A (ko) | 2008-02-04 |
US20090090103A1 (en) | 2009-04-09 |
JPWO2006126646A1 (ja) | 2008-12-25 |
EP1887253A4 (en) | 2010-11-17 |
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