CN103032310A - Hydraulic pump device - Google Patents
Hydraulic pump device Download PDFInfo
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- CN103032310A CN103032310A CN 201210365312 CN201210365312A CN103032310A CN 103032310 A CN103032310 A CN 103032310A CN 201210365312 CN201210365312 CN 201210365312 CN 201210365312 A CN201210365312 A CN 201210365312A CN 103032310 A CN103032310 A CN 103032310A
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- pump
- motor
- gear
- live axle
- motor rotor
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Abstract
The invention provides a hydraulic pump device. A pump assembling space in a pump housing is assembled with a first pump which is driven by a driving shaft connected to an engine, and a second pump which is driven by an electric motor having a motor stator and a motor rotor. The electric motor is assembled in the pump assembling space in a manner of being disposed at the periphery of the second pump. A planetary gear mechanism is disposed among a driving shaft, the second pump and the motor rotor. The torque of the driving shaft is transmitted to the second pump through the planetary gear mechanism.
Description
Technical field
The present invention relates to hydraulic pumping unit.
Background technique
In the past, known following technology namely, when the action of the motor of vehicle, in order to supply with the oil be used to lubricated, the action of carrying out various mechanisms, control etc., was used for the pump case of assembling oil hydraulic pump in the automatic transmission configuration.
The known vehicle that is equipped with idling system, when vehicle temporarily stopped, this idling system temporarily stopped motor.
In the above-mentioned vehicle that is equipped with idling system, owing to temporarily stop (idle stop) of oil hydraulic pump along with motor stops, so can't supply with hydraulic pressure to the clutch mechanism in the automatic transmission etc.
Therefore, in being equipped with the vehicle of idling system, the clutch mechanism of the outer installment that is known in automatic transmission in the automatic transmission etc. supplied with the motor-drive pump of hydraulic pressure.
Yet, in the different vehicle of various forms, there is the situation be difficult to guarantee arrange the space of motor-drive pump, at this moment, can't adopt idling system.
In addition, in the past, for example, as TOHKEMY 2009-191645 communique was disclosed, hydraulic pump drive system had oil hydraulic pump, planetary gears and electric motor.Above-mentioned oil hydraulic pump is discharged working oil to motor and hydraulic operation equipment.Above-mentioned planetary gears is connected with the live axle that is used for the driving oil hydraulic pump, and is connected with motor via main shaft.Above-mentioned electric motor is connected with planetary gears via output shaft.
In the disclosed hydraulic pump drive system of TOHKEMY 2009-191645 communique, can utilize the rotation of the output shaft of electric motor to make the rotation speed change of the live axle of the oil hydraulic pump that is connected with motor via planetary gears.Therefore, adjust by the discharge capacity to the working oil of being discharged by oil hydraulic pump, can suppress oil hydraulic pump and too much discharge the work oil condition.In addition, drive oil hydraulic pump owing to can only utilize electric motor via planetary gears, thereby even in the situation of for example engine stop, also can supply with hydraulic pressure to hydraulic operation equipment.
Yet, in the TOHKEMY 2009-191645 communique, be difficult to assembling electric motor and planetary gears in the pump case of automatic transmission.
Summary of the invention
One of purpose of the present invention is to provide following hydraulic pumping unit, that is, can be easily in the pump assembling space of pump case assembling by the first pump of drive shaft and the second pump by electrical motor driven.
Be characterised in that on the formation of the hydraulic pumping unit of a mode of the present invention, at the pump assembling space of pump case to be assembled with in axial adjacent mode: by the first pump of the drive shaft that is connected with motor; And by the second pump of the electrical motor driven with motor stator and motor rotor, described electric motor is assembled into described pump assembling space in the mode of the periphery that is positioned at described the second pump, between described live axle, described the second pump, described motor rotor three, setting and linking has planetary gears, the moment of torsion of described live axle via described planetary gears to described the second pump transmission.
Description of drawings
By the detailed description of preferred implementation of the present invention being carried out referring to accompanying drawing, further feature of the present invention, advantage can become clearer, and wherein, reference character represents key element of the present invention, wherein:
Fig. 1 is the longitudinal section of the hydraulic pumping unit of expression embodiments of the invention.
Fig. 2 is the longitudinal section that pump case that Watch with magnifier is shown in the hydraulic pumping unit of embodiments of the invention is assembled with the state of the first pump and the second pump.
Fig. 3 is the sectional elevation along the first pump of the III-III line of Fig. 2.
Fig. 4 is the sectional elevation along the second pump of the IV-IV line of Fig. 2.
Fig. 5 is the explanatory drawing of relation of rotating speed (rotating speed of unit time) of internal gear of the sleeve as live axle, motor rotor, second pump of the hydraulic pumping unit of expression embodiments of the invention.
Fig. 6 be the expression embodiments of the invention hydraulic pumping unit as the rotating speed of the sleeve of live axle and the explanatory drawing of the relation of the discharge total amount of the oil that is produced by the first pump and the second pump.
Embodiment
Describe being used for implementing mode of the present invention according to embodiment.
According to Fig. 1 ~ Fig. 6, the hydraulic pumping unit of embodiments of the invention is described.
As shown in Figure 1, in the hydraulic pumping unit of the fluid torque converter 1 that is assembled in automatic transmission, pump case 10 is utilized bolt and is fixed in the shell (not shown) of automatic transmission.Said pump housing 10 by utilize bolt (not shown) with about first, second two housings 11,12 of cutting apart in conjunction with consisting of.First, second two housings 11,12, form pump assembling space 13.More specifically, pump assembling space 13 is by the first housing 11 and central parts the second housing 12 opposed internal faces forming with the first housing 11 opposed internal faces to the axial recessed assembling recess that forms and the second housing 12.
At first, second two housings 11,12 opposed internal face, be formed with respectively suction port 15,17 and exhaust port 16,18.
And, be formed with flange collar 11a in the bottom surface of the assembling recess of the first housing 11, this flange collar 11a be embedded in the external gear 23 of the first pump 20 described later outer circumferential face, and rotatably external gear wheel 23 guide.
In addition, be formed with flange collar 12a at the internal face of the second housing 12, this flange collar 12a be embedded in the external gear 46 of the second pump 40 described later outer circumferential face, and rotatably external gear wheel 46 guide.
In addition, at the central part of the second housing 12, dispose stator main shaft 5 in the mode in the sleeve 2 of fluid torque converter 1.
In addition, among this embodiment 1, the sleeve 2 of fluid torque converter 1 is equivalent to the live axle that is connected with motor.
As shown in Figure 2, in pump assembling space 13, axially to be adjacent to be assembled with the first pump 20 and the second pump 40.The sleeve 2 that above-mentioned the first pump 20 is used as live axle drives.Above-mentioned the second pump 40 is driven by electric motor (reversible motor) 30.Electric motor 30 has motor stator 31 and motor rotor 33.
In addition, electric motor 30 is assembled in pump assembling space 13 in the mode of the periphery that is positioned at the first pump 20 and the second pump 40.
In addition, in 33 in sleeve 2, the second pump 40, motor rotor, be equipped with planetary gears 51.Sleeve 2, the second pump 40, motor rotor 33 link by planetary gears 51.And the moment of torsion of sleeve 2 transmits to the second pump 40 via planetary gears 51.
That is, in the embodiments of the invention, as shown in Figure 2, the motor stator 31 of electric motor 30 has the outside dimension corresponding with the internal diameter size of the inner circle wall face of pump assembling space 13.And motor stator 31 forms has the length dimension almost identical with the axial length dimension of pump assembling space 13.Motor stator 31 is fixed in the peripheral wall surfaces of pump assembling space 13 with the state that can't rotate.
Said motor stator 31 possesses core part 32a and a plurality of coil 32b.Above-mentioned a plurality of coil 32b installs at circumferential a plurality of coil assembly departments of the inner peripheral surface that is formed at above-mentioned core part 32a.
Motor rotor 33 is disposed at the interior week of motor stator 31.Said motor rotor 33 has cylindrical part 34 and plectane section 35.The mode that a plurality of permanent magnets replace with the S utmost point, the N utmost point is along the circumferential configuration of the outer circumferential face of above-mentioned cylindrical part 34.Above-mentioned plectane section 35 is with from forming towards the mode of the outer circumferential face of sleeve 2 near the axial central part of the inner peripheral surface of above-mentioned cylindrical part 34.And, plectane section 35 rotatably is embedded in the outer circumferential face of sleeve 2 outward via following bearing (sliding bearing or rolling bearing) 37, this bearing 37 be arranged on central part and the sleeve 2(of plectane section 35 or be equipped on sleeve 2 identical central lines on axis body, for example, stator main shaft 5) outer circumferential face between.And the first pump 20 and the second pump 40 are by plectane section 35 intervals.
In addition, electric motor 30 is connected with not shown control gear, and controls rotation based on the program of having set.
As shown in Figure 2, the first pump 20 be provided in the assembling recess of the first housing 11 that consists of pump assembling space 13 the bottom surface, and the plectane section 35 of motor rotor 33 between.
As shown in Figure 3, the first pump 20 consists of by having the crescent gear pump of internal gear 21 with external gear 23.Circumferentially be formed with a plurality of external tooths 22 at the outer circumferential face of above-mentioned internal gear 21.The internal tooth 24 that meshes at a plurality of external tooths that circumferentially are formed with a plurality of and above-mentioned internal gear 21 22 of the inner peripheral surface of aforementioned external teeth wheel 23.
And, but sleeve 2 combinations of internal gear 21 transferring power of the first pump 20 ground and fluid torque converter 1.
In addition, the external gear 23 of the first pump 20 with the state of the center of internal gear 21 eccentric (among Fig. 3, with the large small eccentricity of offset A) under, rotatably be embedded in as illustrated in fig. 2 the flange collar 11a of the first housing 11.
And, between the internal tooth 24 of the external tooth 22 of internal gear 21 and external gear 23, be formed with pocketed oil section 25.Internal gear 21 is subject to rotating from the transmission of power of sleeve 2 (moment of torsion transmission), accompanies therewith, and external gear 23 is followed rotation, produces thus pumping action.
In addition, the oil discharge capacity of the first pump 20 is set as following discharge capacity, namely, when the rotating speed of motor (sleeve 2) is idling speed N, can guarantee the oily discharge capacity of needed irreducible minimum.
As shown in Figure 2, the second pump 40 is provided between the plectane section 35 of the internal face of the second housing 12 that consists of pump assembling space 13 and motor rotor 33.
As shown in Figure 4, identical with the first pump 20, the second pump 40 also consists of by having the crescent gear pump of internal gear 41 with external gear 46.Circumferentially be formed with a plurality of external tooths 42 at the outer circumferential face of above-mentioned internal gear 41.The internal tooth 47 of a plurality of external tooths 42 engagements of and internal gear 41 a plurality of circumferentially being formed with of the inner peripheral surface of aforementioned external teeth wheel 46.
In addition, the external gear 46 of the second pump 40 with the state of the center of internal gear 41 eccentric (among the figure, with the large small eccentricity of offset B) under, rotatably be embedded in as illustrated in fig. 2 the flange collar 12a of the second housing 12.
In addition, between the internal tooth 47 of the external tooth 42 of internal gear 41 and external gear 46, be formed with pocketed oil section 48.And along with the rotation of internal gear 41, external gear 46 is followed rotation, produces thus pumping action.
In addition, among this embodiment 1, the internal gear 41 of the second pump 40 and the diameter of external gear 46 form with internal gear 21 and the external gear 23 of the first pump 20 almost identical, and offset A, B also are set as almost identical.
As shown in Figure 2, the second housing 12 side ends at the inner peripheral surface of the internal gear 41 of the second pump 40 are formed with end plate 43, and this end plate 43 is outstanding and be embedded in the outer circumferential face of sleeve 2 rotatably via bearing (sliding bearing or rolling bearing) 45 at central part to radially inner side.
And between the plectane section 35 of end plate 43 and motor rotor 33, formation is useful on the accommodation space 50 of taking in planetary gears 51.
Such as Fig. 2 and shown in Figure 4, planetary gears 51 has sun gear 52, a plurality of planetary pinion 53, as end plate 43 and the internal-gear 56 of the internal gear 41 of planetary carrier 55.But above-mentioned sun gear 52 is located at the outer circumferential face of sleeve 2 with being positioned at accommodation space 50 and transferring power.Above-mentioned planetary pinion 53 and sun gear 52 engagements.Above-mentioned end plate 43 supports a plurality of planetary pinions 53 for rotating centered by central shaft 54.Above-mentioned internal-gear 56 has the internal tooth with 53 engagements of a plurality of planetary pinions, and with the plectane section 35 integrated ground setting of motor rotor 33.
And, when the number of teeth with sun gear 52 be made as Za, with the number of teeth of planetary pinion 53 be made as Zb, with the number of teeth of internal-gear 56 be made as Zc, with the output shaft of sleeve 2(motor) rotating speed be made as ω 1, when the rotating speed of motor rotor 33 is made as ω 3, the second pump 40 is set as with rotating speed shown in Figure 5 driven (rotation).
Namely, as shown in Figure 5, when engine stop (rotating speed of sleeve 2 is 0), make each coil 32b energising of motor stator 31, and make motor rotor 33 to postive direction with rotational speed omega 3 rotation, thus the driving force of motor rotor 33 is passed to the internal-gear 56, planetary pinion 53 of planetary gears 51 and as the internal gear 41 of the second pump 40 of planetary carrier 55.
And the internal gear 41 of the second pump 40 is with the rotation of " (Zc/Za+Zc) * ω 3 " rotating speed.
When motor moves, and when the coil 32b of motor stator 31 is non-power status, driven the internal gear 21 of the first pump 20 by sleeve 2, and, transmit to the sun gear 52 of planetary gears 51, planetary pinion 53 and as the internal gear 41 of the second pump 40 of planetary carrier 55.At this moment, motor rotor 33 remains halted state, accompanies therewith, and the rotating speed of internal-gear 56 remains 0.
Thus, the internal gear 21 of the first pump 20 is with rotational speed omega 1 rotation of motor, and the internal gear 41 of the second pump 40 is with " (Za/Za+Zc) * ω 1 " rotating speed rotation.
When motor moves, switch on by the coil 32b that makes motor stator 31, and make motor rotor 33 to postive direction or driving in the other direction, can make via planetary gears 51 variable speed of the internal gear 41 of the second pump 40.
For example, by making the coil 32b energising of motor stator 31, and making motor rotor 33 to postive direction rotation, the internal-gear 56 that makes planetary gears 51 is to postive direction (direction identical with motor rotor 33) rotation, thereby makes the internal gear 41 speedups ground rotation of the second pump 40.
In contrast, by making the coil electricity of motor stator 31, and make motor rotor 33 to opposite spin, and the internal-gear 56 that makes planetary gears 51 (direction identical with motor rotor 33) rotation in the other direction, thus make the ground rotation of slowing down of the internal gear 41 of the second pump 40.
And, by making motor rotor 33(internal-gear 56) with " (Za/Zc) * and ω 1 " the rotating speed counter-rotating, the rotating speed that makes the internal gear 41 of the second pump 40 is 0.
The hydraulic pumping unit of embodiments of the invention consists of as described above.
Therefore, when motor moves, by the sleeve 2 as live axle the internal gear 21 of the first pump 20 is rotated, drive thus the first pump 20.At this moment, when the coil 32b of motor stator 31 is non-power status, drive the second pump 40 via planetary gears 51.
Therefore, compare with the axial thickness size of the oil hydraulic pump in the past of the pump case 10 that is assembled in automatic transmission, can dwindle with the amount suitable with the oily discharge capacity of the second pump 40 thickness size of the first pump 20.
And owing to dwindle the axial thickness size of the first pump 20, institute is so that the second pump 40 becomes easy to pump case 10 interior assemblings.
When motor moves, switch on by the coil 32b that makes motor stator 31, and make motor rotor 33 to postive direction or driving in the other direction, can make the rotating speed (oily discharge capacity) of the second pump 40 variable via planetary gears 51.
For example, as shown in Figure 6, when motor moves, and when motor is in the low speed rotation zone, the situation of busy shift is arranged.Therefore, it is many that the oil that needs is discharged quantitative change.
Therefore, in the low speed rotation zone of motor, switch on by the coil 32b that makes motor stator 31, and motor rotor 33 is driven to postive direction, correspondingly increase the rotating speed of the internal gear 41 of the second pump 40.Thus, in the low speed rotation zone of motor, guaranteed the oily discharge capacity that needs.
In addition, in the middling speed rotary area of motor, because the needed oily discharge capacity of guaranteeing usually to travel, so the coil 32b of motor stator 31 is non-power status, and the internal gear 41 of the second pump 40 rotates via planetary gears 51.
In addition, in the High Rotation Speed zone of motor, because oily discharge capacity becomes too much easily, institute is so that the coil 32b energising of motor stator 31 and make motor rotor 33 to the opposite direction driving.And, make motor rotor 33 to driving the rotating speed of the internal gear 41 of second pump 40 that correspondingly diminishes in the other direction.
Thus, in the High Rotation Speed zone of motor, can suppress the too much discharge capacity of oil.
When motor temporarily stops (idle stop), by the coil 32b energising that makes motor stator 31 motor rotor 33 is driven to postive direction, can drive via planetary gears 51 the second pump 40.
Thus, when motor temporarily stops (idle stop), can discharge the needed oil masses such as clutch mechanism in the automatic transmission.In addition, when motor temporarily stops (idle stop), compare when moving with motor, the oil mass that needs is few, hydraulic pressure is low.
In the embodiments of the invention, the oil discharge capacity of the first pump 20 is set as following discharge capacity, namely, when the rotating speed of motor is idling speed N, need can guarantee the oily discharge capacity of irreducible minimum.
Therefore, even produce in the bad situation of action at the second pump 40, also can utilize the oily discharge capacity of the first pump 20 to guarantee travelling of vehicle.
In the embodiments of the invention, the plectane section 35 of motor rotor 33 is rotatably supported in the outer circumferential face as the sleeve 2 of live axle via bearing 37.
Thus, motor rotor 33 is not very stably rotated at the center with beating.
In addition, the plectane section 35 of motor rotor 33 is also as the spacing wall of the first pump 20 and the second pump 40 and bring into play function.Therefore, can save and make to be used for interval the first pump 20 and the spacing wall of the special use of the second pump 40 and the trouble of assembling, and owing to the parts number of packages, assemble the minimizing in man-hour and can realize reducing cost.
In the embodiments of the invention, the end plate 43 of inner peripheral surface that is formed at the internal gear 41 of the second pump 40 is rotatably supported in the outer circumferential face as the sleeve 2 of live axle via bearing 45.Thus, the internal gear 41 of the second pump 40 is not very stably rotated at the center with beating.
In addition, in the accommodation space 50 that can between the plectane section 35 of the end plate 43 of the internal gear 41 of the second pump 40 and motor rotor 33, consist of, take in planetary gears 51.
In addition, the end plate 43 of the internal gear 41 of the second pump 40 is as planetary carrier 55 and the performance function, namely, a plurality of planetary pinions 53 are supported a plurality of planetary pinions 53 centered by central shaft 54 rotatably.
In addition, the plectane section 35 of motor rotor 33 is as the support unit of the internal-gear 56 of planetary gears 51 and bring into play function.
Thus, can the accommodation space 50 between the plectane section 35 of the end plate 43 of the internal gear 41 of the second pump 40 and motor rotor 33 in, rationally set and take in planetary gears 51.
In addition, the present invention is not limited to above-described embodiment, in the scope that does not break away from purport of the present invention, can implement in various modes.
Claims (5)
1. a hydraulic pumping unit is characterized in that, at the pump assembling space of pump case to be assembled with in axial adjacent mode: by the first pump of the drive shaft that is connected with motor; And by the second pump of the electrical motor driven with motor stator and motor rotor,
Described electric motor is assembled into described pump assembling space in the mode of the periphery that is positioned at described the second pump, between described live axle, described the second pump, described motor rotor three, setting and linking has planetary gears, the moment of torsion of described live axle via described planetary gears to described the second pump transmission.
2. hydraulic pumping unit according to claim 1 is characterized in that,
The oil discharge capacity of the first pump is set to following discharge capacity, namely, when the rotating speed of motor is idling speed, can guarantee the oily discharge capacity of required irreducible minimum.
3. hydraulic pumping unit according to claim 1 and 2 is characterized in that,
Motor rotor possesses: cylindrical part, at the permanent magnet that circumferentially alternately is equipped with a plurality of S utmost points, the N utmost point of the outer circumferential face of this cylindrical part; And plectane section, this plectane section is with from forming towards the mode of the outer circumferential face of live axle near the axial central part of the inner peripheral surface of this cylindrical part, and be embedded in live axle outside rotatably via bearing or at the outer circumferential face of the axis body that arranges with the same center line of live axle at central part
Utilize described plectane section that the first pump and the second pump is spaced apart.
4. hydraulic pumping unit according to claim 3 is characterized in that,
The second pump is made of crescent gear pump, this crescent gear pump has along the external gear of the internal tooth of a plurality of external tooths engagements of the internal gear that circumferentially is formed with a plurality of external tooths of outer circumferential face and and this internal gear a plurality of along circumferentially being formed with of inner peripheral surface, inner peripheral surface at described internal gear forms end plate, this end plate is outstanding and be embedded in the outer circumferential face of live axle at central part outside rotatably via bearing to radially inner side, is configured for taking in the accommodation space of planetary gears between the plectane section of described end plate and motor rotor.
5. hydraulic pumping unit according to claim 4 is characterized in that,
Planetary gears has:
Sun gear, the outer circumferential face that it is positioned at accommodation space and can be arranged to transferring power live axle;
A plurality of planetary pinions, these a plurality of planetary pinions and the engagement of described sun gear;
As the end plate of the internal gear of planetary carrier, it makes described a plurality of planetary pinion can support rotatably described a plurality of planetary pinion centered by central shaft; And
Internal-gear, it has the internal tooth with described a plurality of planetary pinion engagements, and is located at integratedly the plectane section of motor rotor.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2011212250A JP2013072494A (en) | 2011-09-28 | 2011-09-28 | Oil pump device |
| JP2011-212250 | 2011-09-28 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103032310A true CN103032310A (en) | 2013-04-10 |
Family
ID=46939635
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201210365312 Pending CN103032310A (en) | 2011-09-28 | 2012-09-26 | Hydraulic pump device |
Country Status (2)
| Country | Link |
|---|---|
| JP (1) | JP2013072494A (en) |
| CN (1) | CN103032310A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113309755A (en) * | 2021-06-21 | 2021-08-27 | 浙江大学 | Low-speed large-torque combined hydraulic motor |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112424505A (en) * | 2018-09-14 | 2021-02-26 | 舍弗勒技术股份两合公司 | Positioning convex component, machining method of positioning convex component and hydraulic torque converter |
-
2011
- 2011-09-28 JP JP2011212250A patent/JP2013072494A/en not_active Withdrawn
-
2012
- 2012-09-26 CN CN 201210365312 patent/CN103032310A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113309755A (en) * | 2021-06-21 | 2021-08-27 | 浙江大学 | Low-speed large-torque combined hydraulic motor |
| CN113309755B (en) * | 2021-06-21 | 2022-03-25 | 浙江大学 | Low-speed large-torque combined hydraulic motor |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2013072494A (en) | 2013-04-22 |
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Application publication date: 20130410 |