CN104220750A - Fluid pressure drive unit - Google Patents
Fluid pressure drive unit Download PDFInfo
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- CN104220750A CN104220750A CN201380017785.7A CN201380017785A CN104220750A CN 104220750 A CN104220750 A CN 104220750A CN 201380017785 A CN201380017785 A CN 201380017785A CN 104220750 A CN104220750 A CN 104220750A
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- mentioned
- motor
- fluid
- fluid pressure
- running shaft
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Classifications
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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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/20—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F04B1/22—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block having two or more sets of cylinders or pistons
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0636—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis having rotary cylinder block
- F03C1/0644—Component parts
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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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
- F04B1/128—Driving means
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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
- F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
- F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
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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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/08—Cooling; Heating; Preventing freezing
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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
- F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
- F04B53/18—Lubricating
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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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
- F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
- F05B2210/00—Working fluid
- F05B2210/10—Kind or type
- F05B2210/11—Kind or type liquid, i.e. incompressible
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Details Of Reciprocating Pumps (AREA)
- Reciprocating Pumps (AREA)
- Electromagnetic Pumps, Or The Like (AREA)
Abstract
A fluid pressure drive unit provides working fluid to a fluid pressure actuator and drives the same. The fluid pressure drive unit is provided with the following: a fluid pressure pump that sucks in and ejects the working fluid; an electric motor for rotating and driving the fluid pressure pump; a power transmitting mechanism for transmitting power between the rotation axle of the fluid pressure pump and the rotation axle of the electric motor; and a circulation mechanism that is driven by the power transmitted by the power transmitting mechanism. The circulation mechanism is for cooling the electric motor by introducing fluid for lubrication that is inside of the power transmitting mechanism.
Description
Technical field
The present invention relates to a kind of fluid pressure driver element by carrying out driving to fluid pressure driver supply working fluid.
Background technique
In the past, in the building machineries such as power digger, use a kind of mixed power to construct, this mixed power structure utilizes the residue output power of motor, the exhaust energy of driver makes generator rotate, store the electric power obtained by electrical power generators, and use the work of electric power to driver stored to assist.In such mixed power structure, use a kind of fluid to press driver element, this fluid pressure driver element comprises: motor, and it utilizes the electric power stored to rotate; And service pump, it utilizes motor rotary actuation, and this service pump is assisted by the work of ejection working fluid to the driver utilizing main pump to carry out.
In JP2011-127569A, disclose a kind of auxiliary regeneration device, this auxiliary regeneration device comprises: motor generator set, and it utilizes electric energy rotary work; Me icgcii motor, it utilizes the energy of working fluid to carry out rotary actuation motor generator set; And service pump, it utilizes motor generator set rotary actuation and sprays working fluid.
Summary of the invention
But in the auxiliary regeneration device of JP2011-127569A, dynamoelectric and power generation chance is generated heat when being driven in rotation or when creating regenerated electric power.Therefore, a kind of cooling system using pump to cool motor generator set to make refrigerant circulation from outside is needed.
The present invention puts in view of the above-mentioned problems and makes, and its object is to the cooling mechanism of the motor simplified in fluid pressure driver element.
According to certain mode of execution of the present invention, provide a kind of fluid to press driver element, it is by driving to fluid pressure driver supply working fluid.This fluid pressure driver element comprises: fluid press pump, and it is for sucking and spraying working fluid; Motor, it is for the above-mentioned fluid press pump of rotary actuation; Power transmission mechanism, it is for transferring power between the running shaft and the running shaft of above-mentioned motor of above-mentioned fluid press pump; And cycling mechanism, its by above-mentioned power transmission mechanism the motivational drive of transmitting, this cycling mechanism guides the lubrication fluid in this power transmission mechanism and cools above-mentioned motor.
Embodiments of the present invention, advantage of the present invention is explained referring to accompanying drawing.
Accompanying drawing explanation
Fig. 1 is the plan view of the part cutting the fluid pressure driver element representing embodiments of the present invention open.
Fig. 2 is the II-II sectional view of the fluid press pump motor of Fig. 1.
Fig. 3 is the sectional view of plate, power transmission mechanism and cycling mechanism in Fig. 1.
Embodiment
Hereinafter, with reference to the accompanying drawings of the hydraulic drive unit 100 as fluid pressure driver element of embodiments of the present invention.In hydraulic drive unit 100, use working oil as working fluid.In addition, other fluids such as working water can also be used to replace working oil as working fluid.
First, the structure of hydraulic drive unit 100 is described referring to figs. 1 through Fig. 3.
Hydraulic drive unit 100 is by driving to hydraulic unit driver (omitting diagram) the supply working oil as fluid pressure driver.Hydraulic drive unit 100 is applied to and utilizes the working oil sprayed from the Main Hydraulic Pump driven by prime mover (omitting diagram) to drive the hybrid construction machines such as the power digger of hydraulic unit driver.
As shown in Figure 1, hydraulic drive unit 100 comprises the hydraulic pump motor 1 as fluid press pump motor, and this hydraulic pump motor 1 comprises: as the oil hydraulic pump 10 of fluid press pump, it sucks and sprays working oil; And as the oil hydraulic motor 20 of fluid pressure motor, it is driven in rotation under the effect of the working oil be supplied to.
In addition, hydraulic drive unit 100 comprises: motor 30, and it is to configure with the mode of hydraulic pump motor 1 arranged in parallel; Plate 40, hydraulic pump motor 1 and motor 30 are installed on the same surface of this plate 40; Power transmission mechanism 50, transferring power between the running shaft (omit and illustrate) of its running shaft 2 at hydraulic pump motor 1 and motor 30; And cycling mechanism 60, it cools motor 30 by guiding the lubricant oil as lubrication fluid in power transmission mechanism 50.
The oil hydraulic pump 10 of formation hydraulic pump motor 1 and oil hydraulic motor 20 are respectively the reciprocating pump motor of ramp type capacity-variable type.Compared with oil hydraulic pump 10, oil hydraulic motor 20 is relatively large reciprocating pump motors.
As shown in Figure 2, hydraulic pump motor 1 comprises: shell 3, and it is for receiving oil hydraulic pump 10 and oil hydraulic motor 20; And single running shaft 2, it is supported in shell 3 to rotate mode freely and is common to oil hydraulic pump 10 and oil hydraulic motor 20.
Shell 3 has bolton in the lip part 3a of plate 40.Shell 3 has: supply and discharge path 4, and it feeds to the working oil flowing of oil hydraulic pump 10 and flows for the working oil that self-hydraulic motor 20 is discharged; Ejection path 5, its working oil flowing sprayed for self-hydraulic pump 10; And return path 6, it is supplied to the working oil flowing of oil hydraulic motor 20 for self-hydraulic driver returns.
Supply and discharge path 4 is communicated with the fuel tank (omit and illustrate) for storing working oil.Ejection path 5 is all communicated with hydraulic unit driver with return path 6.Supply and discharge path 4 is set to spray path 5 relative with return path 6.
Oil hydraulic pump 10 and oil hydraulic motor 20 are to configure in the axially relative mode of running shaft 2 across supply and discharge path 4, ejection path 5 and return path 6.
Spray to ejection path 5 after oil hydraulic pump 10 sucks the working oil of supply and discharge path 4.Oil hydraulic pump 10 utilizes the working oil of ejection to assist the driving utilizing Main Hydraulic Pump to carry out hydraulic unit driver.Oil hydraulic pump 10 comprises: cylinder unit 11, and it is linked to running shaft 2; Multiple piston 13, it is accommodated in respectively to divide and is formed in multiple cylinder bodies 12 of cylinder unit 11; Swash plate 14, it moves back and forth with the piston 13 of this swash plate 14 sliding contact for making; And thrust plate 15, the end face sliding contact of itself and cylinder unit 11.
Cylinder unit 11 is formed as roughly cylindric, rotates integratedly with running shaft 2.Utilize running shaft 2 rotary actuation cylinder unit 11.Multiple cylinder body 12 is formed with in the mode parallel with running shaft 2 in cylinder unit 11.
Cylinder body 12 is circumferentially arranged as ring-type at certain intervals same centered by the running shaft 2 of cylinder unit 11.Piston 13 is inserted in each cylinder body 12, divides and be formed with chamber volume 12a between cylinder body 12 and piston 13.Chamber volume 12a is communicated with thrust plate 15 via intercommunicating pore.
When cylinder unit 11 rotates together with running shaft 2, piston 13 and swash plate 14 sliding contact.Thus, piston 13 moves back and forth in cylinder body 12 according to the deflection angle of swash plate 14, and makes chamber volume 12a expand or reduce.
Swash plate 14 is set to and can utilizes capacity switching driver (omitting diagram) adjustment deflection angle.Swash plate 14 can deflect to the state shown in Fig. 2 from vertical relative to running shaft 2, that deflection angle is zero state.Utilize the deflection angle of capacity switching driver stepless changing swash plate 14.
Thrust plate 15 is formed as discoideus, and its center has the through hole run through for running shaft 2.Thrust plate 15 has: supplying mouth 15a, and it is formed as the arc-shaped centered by running shaft 2 and supply and discharge path 4 is communicated with chamber volume 12a; And ejiction opening 15b, it is formed as the arc-shaped centered by running shaft 2 equally and ejection path 5 is communicated with chamber volume 12a.
In oil hydraulic pump 10, piston 13 and swash plate 14 sliding contact and region that chamber volume 12a expands is inhalation area, piston 13 and swash plate 14 sliding contact and region that chamber volume 12a reduces are for spray region.Supplying mouth 15a is formed as corresponding with inhalation area, and ejiction opening 15b is formed as with to spray region corresponding.Thus, along with the rotation of cylinder unit 11, working oil is inhaled in the chamber volume 12a of supplying mouth 15a, and working oil sprays from the face of the chamber volume 12a of ejiction opening 15b.
The working oil utilizing self-hydraulic driver to discharge carrys out rotary actuation oil hydraulic motor 20.Oil hydraulic motor 20 comprises: cylinder unit 21, and it is linked to running shaft 2; Multiple piston 23, it is accommodated in respectively to divide and is formed in multiple cylinder bodies 22 of cylinder unit 21; Swash plate 24, it is for moving back and forth with the piston 23 of this swash plate 24 sliding contact; And thrust plate 25, the end face sliding contact of itself and cylinder unit 21.Only size is different from the structure of above-mentioned oil hydraulic pump 10 for the structure of the cylinder unit 21 of oil hydraulic motor 20, cylinder body 22, piston 23 and swash plate 24, and other aspects are identical with the structure of above-mentioned oil hydraulic pump 10, therefore in this description will be omitted.
Thrust plate 25 is formed as discoideus, and its center has the through hole run through for running shaft 2.Thrust plate 25 has: supplying mouth 25a, and it is formed as the arc-shaped centered by running shaft 2 and return path 6 is communicated with chamber volume 22a; And exhaust port 25b, it is formed as the arc-shaped centered by running shaft 2 equally and supply and discharge path 4 is communicated with chamber volume 22a.
In oil hydraulic motor 20, piston 23 and swash plate 24 sliding contact and region that chamber volume 22a expands is inhalation area, piston 23 and swash plate 24 sliding contact and region that chamber volume 22a reduces is discharging area.Supplying mouth 25a is formed as corresponding with inhalation area, and exhaust port 25b is formed as corresponding with discharging area.Thus, along with the rotation of cylinder unit 21, working oil is inhaled in the chamber volume 22a of supplying mouth 25a, and working oil is discharged from the face of the chamber volume 22a of exhaust port 25b.
Motor 30 rotary actuation oil hydraulic pump 10, and the rotation of oil hydraulic motor 20 can be utilized to produce regenerated electric power.The electrical power storage that obtains is generated electricity in electric accumulator (omitting diagram) by motor 30.Motor 30 uses and utilizes the rotation of oil hydraulic motor 20 to regenerate and the regenerated electric power that is stored in electric accumulator carrys out rotary actuation oil hydraulic pump 10.
As shown in Figure 1, plate 40 is tabular component, and one side 40a is provided with hydraulic pump motor 1 and motor 30, and another side 40b is provided with the shell 51 of power transmission mechanism 50.Thus, power transmission mechanism 50 is so that across plate 40, the mode relative with motor 30 with hydraulic pump motor 1 is arranged.At the through hole (omitting diagram) that plate 40 is formed with through hole (omitting diagram) that the running shaft 2 for hydraulic pump motor 1 runs through, the running shaft of electric motor 30 runs through and for the refluxing opening 42 (with reference to Fig. 3) motor 30 being carried out to cooled oil return.
As mentioned above, in hydraulic drive unit 100, hydraulic pump motor 1 and motor 30 are configured to U-shaped by plate 40 and power transmission mechanism 50.Therefore, it is possible to the entire length of hydraulic drive unit 100 is shortened be equivalent to the mode of arranged in parallel configure hydraulic pump motor 1 and motor 30 the amount of shortening length.Thus, the installation to hybrid construction machine of hydraulic drive unit 100 can be improved.
In addition, also hydraulic pump motor 1 can be arranged on a side 40a of plate 40, another side 40b motor 30 being arranged on plate 40 replaces configuring with U-shaped.In addition, can also by hydraulic pump motor 1 and motor 30 with the mode arranged in series across plate 40.
As shown in Figure 3, power transmission mechanism 50 comprises: shell 51, and it is fixed on plate 40; First gear 52, the running shaft 2 of itself and hydraulic pump motor 1 rotates integratedly; Second gear 53, the running shaft of itself and motor 30 rotates integratedly; And idle pulley 54, it is located between the first gear 52 and the second gear 53 for transferring power.
Shell 51 is for receiving the first gear 52, second gear 53 and idle pulley 54.The state bolton that shell 51 abuts against with the another side 40b of its open end 51a and plate 40 is in the another side 40b of plate 40.Lubricant oil is filled in the inside of shell 51.Shell 51 has through hole 51b, and this through hole 51b is formed at and runs through with the end face of open end 51a opposition side and for the running shaft of idle pulley 54.
First gear 52 has recess 52a, and this recess 52a is formed on the running shaft of the first gear 52, and the running shaft 2 of hydraulic pump motor 1 is intercalated in this recess 52a.Thus, the first gear 52 rotates integratedly with the running shaft 2 of hydraulic pump motor 1.One end of the running shaft of the first gear 52 utilizes clutch shaft bearing 52b to be supported on plate 40 to rotate mode freely, and the other end of the running shaft of the first gear 52 utilizes the second bearing 52c to be supported on shell 51 to rotate mode freely.
Equally, the second gear 53 has recess 53a, and this recess 53a is formed on the running shaft of the second gear 53, and the running shaft of motor 30 is intercalated in this recess 53a.Thus, the second gear 53 rotates integratedly with the running shaft of motor 30.One end of the running shaft of the second gear 53 utilizes clutch shaft bearing 53b to be supported on plate 40 to rotate mode freely, and the other end of the running shaft of the second gear 53 utilizes the second bearing 53c to be supported on shell 51 to rotate mode freely.
Idle pulley 54 is meshed with the first gear 52 and the second gear 53 and mutual transferring power respectively.One end of the running shaft of idle pulley 54 utilizes clutch shaft bearing 54b and is supported on plate 40 to rotate mode freely, and the substantial middle position of the running shaft of idle pulley 54 utilizes the second bearing 54c and is supported on shell 51 to rotate mode freely.The other end of the running shaft of idle pulley 54 runs through through hole 51b and extended in the shell 61 of cycling mechanism 60.
So, by being provided with idle pulley 54 between the first gear 52 and the second gear 53, even if when distant between hydraulic pump motor 1 and motor 30, the diameter of the first gear 52 and the second gear 53 also can be suppressed to become large.Thus, can by power transmission mechanism 50 miniaturization, and can by hydraulic drive unit 100 integral miniaturization.
In addition, by adjusting the gear ratio between the first gear 52 and the second gear 53, the reduction speed ratio between hydraulic pump motor 1 and motor 30 can be set as appropriate value.
Cycling mechanism 60 comprises: shell 61, and its inside is communicated with the inside of the shell 51 of power transmission mechanism 50; Impeller 62, it is as rotating member, rotates integratedly in shell 61 with idle pulley 54; Supply line 63, it guides to motor 30 for the lubrication fluid lifted up by impeller 62; And reflow line 64, it is for returning to the lubrication fluid guiding to motor 30 in power transmission mechanism 50.
The state that shell 61 abuts against with the shell 51 of open end 61a and power transmission mechanism 50 is fixed.The lubricant oil being filled in the inside of the shell 51 of power transmission mechanism 50 flow into the inside of shell 61.In addition, be provided with the 3rd bearing 54d in shell 61, the 3rd bearing 54d is to rotate the other end that mode freely supports the running shaft of idle pulley 54.
Impeller 62 is the coaxial impeller arranged with idle pulley 54.Impeller 62 is installed on the running shaft of idle pulley 54.Impeller 62 is located at for supporting between the second bearing 54c of idle pulley 54 and the 3rd bearing 54d.In addition, impeller 62 can be arranged on the arbitrary position between clutch shaft bearing 54b and the 3rd bearing 54d.
When power transmission mechanism 50 is between hydraulic pump motor 1 and motor 30 during transferring power, impeller 62 rotates, and is lifted up by the lubricant oil be directed in shell 51 in shell 61, power transmission mechanism 50 towards periphery.The rotating speed of impeller 62 rises along with the rotating speed rising of motor 30.Therefore, the amount of the lubricant oil lifted up by impeller 62 becomes many along with the increase of the heating value of motor 30.
Because impeller 62 and idle pulley 54 rotate integratedly, therefore, it is possible to utilize flywheel effect to reduce the rotation inequality of idle pulley 54.Therefore, it is possible to reduce the noise caused by the rotation inequality of idle pulley 54.
In addition, also impeller 62 can be set to and rotate integratedly to replace being set to rotate integratedly with idle pulley 54 with the first gear 52 or the second gear 53.In addition, also can such as impeller 62 etc. be set at the first gear 52 and the second gear 53, multiple impeller 62 is set respectively.That is, in impeller 62 and the first gear 52, second gear 53 and idle pulley 54 at least any one rotates integratedly.
In addition, also can be arranged through and utilize the rotation of idle pulley 54 and carry out driving thus lift up other the mechanism such as cylinder body of lubricant oil to replace impeller 62.That is, as long as the rotary motion of idle pulley 54 is carried out changing and the mechanism of lubricant oil can be lifted up, can be just any mechanism.
As shown in Figure 1, supply line 63 is for being drawn out to outside and the pipe arrangement of outer ties with motor 30 from shell 61.The surface of the periphery in the face of impeller 62 of supply line 63 in shell 61 is drawn.Be supplied to the oil jacket (omitting diagram) being formed at motor 30 inside via the lubricant oil that supply line 63 is directed, thus motor 30 is cooled.
Reflow line 64 is for being drawn out to outside and the pipe arrangement that links with the refluxing opening 42 (with reference to Fig. 3) being formed at plate 40 from motor 30.Reflow line 64 makes the oil return of discharging from the oil jacket of motor 30 in the shell 51 of power transmission mechanism 50.In addition, the inside that supply line 63 and reflow line 64 can also be formed in the shell of motor 30 replaces supply line 63 and reflow line 64 to be arranged on the structure of the outside of motor 30.
Then, the action of hydraulic drive unit 100 is described.
In hydraulic drive unit 100 to when utilizing Main Hydraulic Pump to assist the driving that hydraulic unit driver carries out, use the electric power be stored in advance in electric accumulator that motor 30 is rotated.Utilize the rotation of motor 30, carry out the running shaft 2 of rotary actuation hydraulic pump motor 1 by power transmission mechanism 50.
Oil hydraulic pump 10 utilizes capacity switching driver to make the deflection angle of swash plate 14 switch to the predetermined value being greater than zero.In oil hydraulic pump 10, piston 13 moves back and forth in cylinder body 12 along with the rotation of cylinder unit 11.By moving back and forth of this piston 13, the working oil from fuel tank is made to be sucked into chamber volume 12a via the supplying mouth 15a of thrust plate 15.Then, ejection path 5 is directed to from the working oil of chamber volume 12a ejection via the ejiction opening 15b of thrust plate 15.
Thus, the working oil that self-hydraulic driver element 100 sprays is supplied to driving hydraulic unit driver, thus to utilizing Main Hydraulic Pump to assist the driving that hydraulic unit driver carries out.
If motor 30 rotary actuation hydraulic pump motor 1, then the rotation of the second gear 53 is passed to idle pulley 54, and the rotation of idle pulley 54 is passed to the first gear 52.The impeller 62 of cycling mechanism 60 rotates along with the rotation of idle pulley 54.
If impeller 62 rotates, then the lubricant oil be directed to via through hole 51b in the shell 51 of the power transmission mechanism 50 in the shell 61 of cycling mechanism 60 is lifted up, and is supplied to the oil jacket of motor 30 via supply line 63.Therefore, utilize the heat exchange between lubricant oil and motor 30, can cool motor 30.The lubricant oil that motor 30 cools is back in the shell 51 of power transmission mechanism 50 via reflow line 64 from the oil jacket of motor 30.
As mentioned above, when motor 30 rotary actuation hydraulic pump motor 1, impeller 62 rotates along with utilizing the transmission to power of power transmission mechanism 50, and lubricant oil is directed to motor 30.Thus, owing to need not arrange from the outside cooling system cooled motor 30, therefore, it is possible to simplify the cooling mechanism of the motor 30 in hydraulic drive unit 100.
In addition, can only when power transmission mechanism 50 transferring power, motor 30 rotates and adstante febre supply lubricant oil and cooling.Thus, compared with the situation using the certainly outside cooling system cooled motor 30 to cool all the time, cooling effectiveness can be improved.
In addition, by making the lubricant oil lifted up by impeller 62 reflux after cooling motor 30, and the lubricant oil in power transmission mechanism 50 can be made to circulate.Therefore, lubricant oil flows in power transmission mechanism 50.Thus, can prevent each bearing supporting the first gear 52, second gear 53 and idle pulley 54 for axle from because lubricant oil is not enough, seizure occurring.
Now, oil hydraulic motor 20 utilizes capacity switching driver to make the deflection angle of swash plate 24 remain zero.Therefore, because piston 23 can not move back and forth in cylinder body 22, the discharge capacity produced because of piston 23 is zero.Thus, oil hydraulic motor 20 is only dally under the prerequisite of not supply and discharge working oil, therefore, it is possible to suppress the driving loss of oil hydraulic motor 20.
On the other hand, when the working oil utilizing self-hydraulic driver to discharge produces regenerated electric power, oil hydraulic motor 20 can utilize capacity switching driver to make the deflection angle of swash plate 24 switch to the predetermined value being greater than zero.In oil hydraulic motor 20, piston 23 moves back and forth in cylinder body 22 along with the rotation of cylinder unit 21.By moving back and forth of this piston 23, self-hydraulic driver returns the oily supplying mouth 25a via thrust plate 25 of the pressurized operation come via return path 6 and flows into chamber volume 22a.Then, piston 23 moves back and forth and rotary actuation cylinder unit 21 in cylinder body 22.The working oil flowing into chamber volume 22a is discharged to supply and discharge path 4 via the exhaust port 25b of thrust plate 25, and is back to fuel tank.
Running shaft 2 and cylinder unit 21 rotate integratedly.The rotation of running shaft 2 is passed to the running shaft of motor 30 by power transmission mechanism 50.Thus, motor 30 can produce regenerated electric power and regenerated electric power is stored to electric accumulator.
If the rotation of the running shaft 2 of hydraulic pump motor 1 is passed to motor 30, then the rotation of the first gear 52 is passed to idle pulley 54, and the rotation of idle pulley 54 is passed to the second gear 53.By the rotation of idle pulley 54, the impeller 62 of cycling mechanism 60 is rotated.Therefore, identical with the situation of motor 30 rotary actuation hydraulic pump motor 1, the heat exchange between lubricant oil and motor 30 can be utilized to cool motor 30.
Now, oil hydraulic pump 10 can utilize capacity switching driver to make the deflection angle of swash plate 14 remain zero.Therefore, because piston 13 can not move back and forth in cylinder body 12, the discharge capacity produced because of piston 13 is zero.Thus, oil hydraulic pump 10 is only dally under the prerequisite of not supply and discharge working oil, therefore, it is possible to suppress the driving loss of oil hydraulic pump 10.
In addition, when hydraulic drive unit 100 to utilize Main Hydraulic Pump to carry out assist to multiple hydraulic unit driver supply working oil, hydraulic drive unit 100 also can assist the driving to a hydraulic unit driver sometimes, and working oil is refluxed from other hydraulic unit drivers.
According to above mode of execution, effect shown below can be played.
Be provided with cycling mechanism 60, this cycling mechanism 60 cools motor 30 by utilizing the rotation of impeller 62 to guide the lubricant oil in power transmission mechanism 50.This impeller 62 and between the first gear 52 and the second gear 53 idle pulley 54 of transferring power rotate integratedly.Therefore, when motor 30 rotary actuation hydraulic pump motor 1, impeller 6 rotates along with power transmission mechanism 50 transferring power, lubricant oil is guided to motor 30.Thus, need not arrange from the outside cooling system cooled motor 30, therefore, it is possible to simplify the cooling mechanism of the motor 30 in hydraulic drive unit 100.
Above, describe embodiments of the present invention, but above-mentioned mode of execution illustrate only a part for application examples of the present invention, its aim does not also lie in concrete structure technical scope of the present invention being defined in above-mentioned mode of execution.
Such as, hydraulic drive unit 100 for utilizing Main Hydraulic Pump to assist the driving that hydraulic unit driver carries out, but also can replace this situation, and is set to and only uses hydraulic drive unit 100 to drive the structure of hydraulic unit driver.
In addition, oil hydraulic pump 10 and oil hydraulic motor 20 are the reciprocating pump motor of ramp type jointly, as long as but inlet capacity, ejection capacity can be adjusted to zero capacity-variable type, also can be other form.In addition, can also make cycling mechanism 60 that lubricant oil is supplied to hydraulic pump motor 1.
The application is based on the Japanese Patent Application 2012-075565 CLAIM OF PRIORITY of on March 29th, 2012 to Japanese Patent Office application, and the full content of this application is by referring to being programmed in this specification.
The exclusive character that this inventive embodiment comprises or feature request right as follows.
Claims (7)
1. a fluid pressure driver element, it is by driving to fluid pressure driver supply working fluid, and wherein, this fluid pressure driver element comprises:
Fluid press pump, it is for sucking and spraying working fluid;
Motor, it is for the above-mentioned fluid press pump of rotary actuation;
Power transmission mechanism, it is for transferring power between the running shaft and the running shaft of above-mentioned motor of above-mentioned fluid press pump; And
Cycling mechanism, its by above-mentioned power transmission mechanism the motivational drive of transmitting, this cycling mechanism guides the lubrication fluid in this power transmission mechanism and cools above-mentioned motor.
2. fluid pressure driver element according to claim 1, wherein,
Above-mentioned power transmission mechanism comprises: the first gear, and the running shaft of itself and above-mentioned fluid press pump rotates integratedly; Second gear, the running shaft of itself and above-mentioned motor rotates integratedly; And idle pulley, it is located between above-mentioned first gear and above-mentioned second gear for transferring power;
Above-mentioned cycling mechanism has rotating member, and at least one in this rotating member and above-mentioned first gear, above-mentioned second gear and above-mentioned idle pulley rotates integratedly and lifts up the lubrication fluid in above-mentioned power transmission mechanism.
3. fluid pressure driver element according to claim 2, wherein,
Above-mentioned cycling mechanism comprises:
Supply line, it guides to above-mentioned motor for the lubrication fluid lifted up by above-mentioned rotating member; And
Reflow line, it is for returning to the lubrication fluid guiding to above-mentioned motor in above-mentioned power transmission mechanism.
4. fluid pressure driver element according to claim 2, wherein,
Above-mentioned rotating member is the impeller rotated integratedly with above-mentioned idle pulley.
5. fluid pressure driver element according to claim 1, wherein,
Above-mentioned motor to configure with the mode of above-mentioned fluid press pump arranged in parallel,
This fluid pressure driver element also comprises plate, and above-mentioned fluid press pump and above-mentioned motor are installed on the same surface of this plate, and the running shaft of above-mentioned fluid press pump and the running shaft of above-mentioned motor run through this plate.
6. fluid pressure driver element according to claim 1, wherein,
This fluid pressure driver element also comprises fluid pressure motor, and this fluid pressure motor and above-mentioned fluid press pump use same running shaft, and utilizes the working fluid be supplied to carry out this fluid pressure motor of rotary actuation,
Above-mentioned motor can utilize the rotation of above-mentioned fluid pressure motor to produce regenerated electric power.
7. fluid pressure driver element according to claim 6, wherein,
This fluid pressure driver element is applied to hybrid construction machine, and this hybrid construction machine utilizes the working fluid sprayed from the main fluid press pump by prime mover driven to drive above-mentioned fluid to press driver,
Above-mentioned fluid pressure motor is pressed the working fluid rotary actuation of driver discharge from above-mentioned fluid,
Above-mentioned motor utilizes the rotation of above-mentioned fluid pressure motor to produce regenerated electric power, and uses this regenerated electric power to carry out the above-mentioned fluid press pump of rotary actuation,
Above-mentioned fluid press pump utilizes the working fluid of ejection to assist the driving that above-mentioned fluid pressure driver carries out utilizing above-mentioned main fluid press pump.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2012-075565 | 2012-03-29 | ||
| JP2012075565A JP5767996B2 (en) | 2012-03-29 | 2012-03-29 | Fluid pressure drive unit |
| PCT/JP2013/058254 WO2013146576A1 (en) | 2012-03-29 | 2013-03-22 | Fluid pressure drive unit |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104220750A true CN104220750A (en) | 2014-12-17 |
| CN104220750B CN104220750B (en) | 2016-07-20 |
Family
ID=49259831
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380017785.7A Expired - Fee Related CN104220750B (en) | 2012-03-29 | 2013-03-22 | Fluid pressure driver element |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US20150064030A1 (en) |
| EP (1) | EP2848808B1 (en) |
| JP (1) | JP5767996B2 (en) |
| KR (1) | KR101782684B1 (en) |
| CN (1) | CN104220750B (en) |
| WO (1) | WO2013146576A1 (en) |
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| CN112879256A (en) * | 2021-03-10 | 2021-06-01 | 焦秀智 | Experimental device capable of simulating reservoir pressure |
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Also Published As
| Publication number | Publication date |
|---|---|
| EP2848808A4 (en) | 2016-03-30 |
| JP5767996B2 (en) | 2015-08-26 |
| KR20140129274A (en) | 2014-11-06 |
| KR101782684B1 (en) | 2017-09-27 |
| US20150064030A1 (en) | 2015-03-05 |
| CN104220750B (en) | 2016-07-20 |
| EP2848808A1 (en) | 2015-03-18 |
| EP2848808B1 (en) | 2018-07-04 |
| WO2013146576A1 (en) | 2013-10-03 |
| JP2013204541A (en) | 2013-10-07 |
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