CN107246467B - Stepless transmission device for hydraulic machinery of loader - Google Patents
Stepless transmission device for hydraulic machinery of loader Download PDFInfo
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- CN107246467B CN107246467B CN201710299575.1A CN201710299575A CN107246467B CN 107246467 B CN107246467 B CN 107246467B CN 201710299575 A CN201710299575 A CN 201710299575A CN 107246467 B CN107246467 B CN 107246467B
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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
- F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
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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
- F16H47/04—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion
- F16H2047/045—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the volumetric type the mechanical gearing being of the type with members having orbital motion the fluid gearing comprising a plurality of pumps or motors
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Abstract
the invention discloses a loader hydraulic mechanical stepless transmission device, comprising: the speed-regulating planetary gear transmission mechanism comprises a hydraulic speed-regulating loop, a planetary distributing and converging mechanism, a hydraulic mechanical fixed shaft gear transmission mechanism and a reverse gear mechanism. The transmission device adopts a planetary mechanism to converge hydraulic power and mechanical power, is formed by connecting three hydraulic mechanical sections in a torque-dividing, speed-converging and power-dividing mode, and is respectively used for starting, low-speed operation and high-speed walking; the reverse gear comprises two hydro-mechanical segments. The transmission device can obtain higher transmission efficiency compared with a hydromechanical power shift gearbox because no circulating power exists in each hydromechanical section. And only 1 clutch needs to be operated during the switching between the sections, so that the smooth switching can be realized.
Description
Technical Field
The invention relates to a stepless transmission device, in particular to a stepless transmission device suitable for hydraulic machinery of a loader.
Background
at present, a hydraulic mechanical power gear shifting gearbox is generally adopted by an engineering mechanical loader, and due to the requirement of loading operation, the speed and the load of an engine change violently, and the efficiency of a hydraulic torque converter is low, the highest transmission efficiency of a transmission system is about 75%.
The hydrostatic transmission can conveniently realize stepless speed regulation, so that the engine of the loader normally works in an economic rotating speed range, and the energy utilization efficiency of the whole vehicle can be improved; however, the efficiency of a hydraulic pump motor closed speed regulation loop used for hydrostatic transmission is also low, so that the lifting potential of the hydrostatic transmission is limited compared with a power shift hydraulic mechanical gearbox.
the hydraulic mechanical transmission can realize high-efficiency stepless transmission by compounding mechanical power and hydraulic power, so that an engine maintains stable load, the improvement of fuel economy is facilitated, the hydraulic mechanical transmission becomes one of the development directions of a loader transmission system, and engineering machinery manufacturers at home and abroad actively develop the research of the transmission technology.
CN 104136812A, CN 104136813A, US2006/0276291 a1 of carte miller, both disclose a multi-gear hydromechanical transmission for a loader, which comprises two continuously variable speed hydromechanical sections and a high-speed hydromechanical section, wherein the two continuously variable speed hydromechanical sections are respectively used for starting and low-speed operation, and the high-speed hydromechanical section is used for walking and turning. Because two paths of hydraulic mechanical power are compounded, the hydraulic path only transmits partial power, and the transmission efficiency is greatly improved compared with a hydraulic mechanical power gear shifting gearbox.
the ZF company US 8328676B 2 discloses a loader hydraulic mechanical transmission device, which adopts two or three hydraulic mechanical sections, adopts a power split mode of speed division and speed convergence (Output split) and speed division and speed convergence (Compound split), and has higher transmission efficiency. But the power of hydraulic elements required by the transmission scheme of the two hydraulic mechanical sections is larger; the speed of the hydraulic element is discontinuous in the switching between the II section and the III section of the three hydraulic mechanical section transmission schemes.
dana Rexroth company US 2014/0305113 a1 discloses a two-stage hydraulic mechanical transmission, a pure hydraulic stage starting and a hydraulic mechanical stage operating and traveling. Dana Rexroth company EP 2280192B1 discloses a three-section type hydraulic mechanical transmission device, wherein a pure hydraulic section starts, two hydraulic mechanical sections are used for operation and walking respectively, and high transmission efficiency can be obtained. However, the two schemes adopt hydraulic section starting, and the efficiency is lower than that of hydraulic mechanical section starting.
Disclosure of Invention
In view of the above, the invention provides a loader hydraulic mechanical stepless transmission device, which adopts a planetary transmission splitting and converging mechanism to realize three hydraulic mechanical sections which are respectively used for starting, low-speed operation and high-speed walking; the hydraulic machinery starts, so that the low-speed transmission efficiency can be improved; the section switching only needs to operate 1 clutch, and smooth switching can be realized.
the loader hydraulic mechanical stepless transmission device comprises: the speed-regulating planetary transmission mechanism comprises a hydraulic speed-regulating loop, a planetary distributing and converging mechanism, a first-section fixed shaft gear transmission mechanism of hydraulic machinery, a second-section fixed shaft gear transmission mechanism of the hydraulic machinery, a third-section fixed shaft gear transmission mechanism of the hydraulic machinery and a reverse gear mechanism;
The hydraulic speed regulation loop comprises: a closed hydraulic circuit consisting of a hydraulic pump and a hydraulic motor; the hydraulic pump is connected with a shaft fixedly connected with a gear R; the gear R is meshed with a gear S fixedly connected to the input shaft; after the power of the engine is input from the input shaft, one part of the power enters a closed hydraulic loop through the hydraulic pump to convert mechanical energy into hydraulic energy, and then enters a branch and confluence mechanism through a gear D connected to a power output shaft of the hydraulic motor to carry out power confluence;
the planet distributing and converging mechanism comprises three planet rows, a gear A, a gear B, a gear C, a gear P and a gear Q; the gear C, the first planet row gear ring and the third planet row planet carrier are coaxially and fixedly connected, and the gear C is meshed with the gear S; the first planet row planet carrier, the third planet row gear ring, the second planet row planet carrier and the gear A are fixedly connected; the third planet row sun gear, the second planet row sun gear and the gear P are fixedly connected; the gear B meshed with the gear D is fixedly connected with a first planet row sun gear; the second planet row gear ring is fixedly connected with the gear Q;
I section dead axle gear drive of hydraulic machinery includes: the planetary power transmission mechanism comprises a gear M meshed with a gear Q in the planetary distributing and converging mechanism, a gear E connected with the gear M through a clutch KV1, and a gear H meshed with the gear E;
II sections dead axle gear drive of hydraulic machinery include: the planetary power transmission mechanism comprises a gear N meshed with a gear P in the planetary distributing and converging mechanism, a gear E connected with the gear N through a clutch KV2, and a gear H meshed with the gear E;
III sections dead axle gear drive of hydraulic machinery includes: the planetary power transmission mechanism comprises a gear G meshed with a gear A in the planetary distributing and converging mechanism, a gear I meshed with the gear G, and a gear H connected with the gear I through a clutch KV 3;
the gear H is meshed with a gear J fixedly connected to the output shaft;
The reverse gear mechanism comprises: a gear K meshing with the gear M, a gear L meshing with the gear N, and a gear F meshing with the gear H; the gear K is connected with the gear F through a reverse clutch KR1, and the gear L is connected with the gear F through a reverse clutch KR 2.
The hydraulic speed regulating circuit also comprises: and the oil replenishing pump maintains the low-pressure of the closed hydraulic loop and provides control oil pressure for the hydraulic pump.
the forward gear of the stepless transmission device comprises three hydraulic mechanical sections which are respectively used for starting, low-speed operation and high-speed walking;
For launch, the clutch KV1 is engaged; the mechanical power entering the planetary distributing and converging mechanism from the gear and the hydraulic power entering the planetary distributing and converging mechanism from the gear B are converged in the planetary distributing and converging mechanism, output from the gear Q and then transmitted to an output shaft through the gear M, the clutch KV1, the gear E, the gear H and the gear J in sequence;
For low speed operation, the clutch KV2 is engaged; the mechanical power entering the planetary distributing and converging mechanism from the gear and the hydraulic power entering the planetary distributing and converging mechanism from the gear B are converged in the planetary distributing and converging mechanism, then are output from the gear P and are transmitted to an output shaft through the gear N, the clutch KV2, the gear E, the gear H and the gear J in sequence;
For high-speed walking, the clutch KV3 is engaged; the mechanical power entering the planetary distributing and converging mechanism from the gear and the hydraulic power entering the planetary distributing and converging mechanism from the gear B are converged in the planetary distributing and converging mechanism, output from the gear A and then transmitted to the output shaft through the gear G, the gear I, the clutch KV3, the gear H and the gear J in sequence.
The stepless transmission device is provided with two reverse gear hydraulic mechanical sections:
When the reverse clutch KR1 is engaged, the continuously variable transmission is in a reverse hydraulic machine I section; the power from the planetary distributing and converging mechanism is input into a reverse gear mechanism through the gear M and then is transmitted to an output shaft through the gear K, a reverse clutch KR1, the gear F, the gear H and the gear J in sequence;
when the reverse clutch KR2 is engaged, the continuously variable transmission is in the reverse hydraulic machine stage ii: the power from the planetary distributing and converging mechanism is input into a reverse gear mechanism through the gear N, and then is transmitted to an output shaft through the gear L, the reverse clutch KR2, the gear F, the gear H and the gear J in sequence.
has the advantages that:
(1) The hydraulic and mechanical power combination is adopted, the hydraulic circuit only transmits partial power, most of the power is transmitted through the mechanical circuit, high transmission efficiency and stepless speed change are realized, the working efficiency can be improved, and the oil consumption of an engine can be reduced.
(2) The planetary splitting and converging mechanism is adopted, and a splitting and converging speed power splitting mode is adopted, so that three hydraulic mechanical sections can be realized, wherein the first hydraulic mechanical section is used for starting, the second hydraulic mechanical section is used for low-speed operation, and the third hydraulic mechanical section is used for high-speed walking; the hydraulic machinery starts, so that the low-speed transmission efficiency can be improved; the section switching only needs to operate 1 clutch, and smooth switching can be realized.
(3) The whole course stepless speed regulation can make the engine work at the economical speed, improve the fuel economy and reduce the noise of the engine.
(4) The zero-speed-difference switching of the clutch between the sections can be realized among the hydraulic mechanical sections, the clutch is suitable for working conditions, the service life of the friction plate of the clutch is prolonged, and the design of a gear shifting logic and an operating system is simplified. Between the hydraulic mechanical sections, because of the existence of the hydraulic speed regulating system, the power gear shifting can be realized, the clutch at the next section is firstly jointed, and then the clutch at the previous section is loosened, thereby ensuring the uninterrupted output of the power and ensuring the operating efficiency.
(5) except the branch and confluence mechanism, other parts adopt fixed-axis gear transmission, on one hand, the center distance reduction of input and output of the loader transmission device can be realized, and on the other hand, the process and the processing cost can be reduced.
Drawings
FIG. 1 is a schematic drive diagram of the hydromechanical compound continuously variable transmission;
Wherein: 1-shell, 2-hydraulic pump, 3-oil supplementing pump, 4-gear S, 5-input shaft, 6-gear A, 7-gear B, 8-gear C, 9-first planet row sun gear, 10-first planet row planet carrier, 11-hydraulic motor, 12-first planet row gear ring, 13-gear D, 14-gear E, 15-gear F, 16-gear G, 17-gear H, 18-clutch KV3, 19-gear I, 20-gear J, 21-output shaft, 22-gear K, 23-gear L, 24-reverse clutch KR2, 25-reverse clutch KR1, 26-gear M, 27-gear N, 28-clutch KV2, 29-clutch KV1, 30-second planet row gear ring, 31-second planet row planet carrier, 32-second planet row sun gear, 34-gear P, 35-gear Q, 37-shaft A, 38-third planet row sun gear, 39-third planet row planet carrier, 40-third planet row gear ring, 41-gear R and 42-shaft B
Detailed Description
The invention is described in detail below by way of example with reference to the accompanying drawings.
The embodiment provides a three-section hydraulic mechanical composite stepless transmission device for a loader, which comprises three hydraulic mechanical sections, wherein the hydraulic mechanical sections are adopted for starting, and the transmission efficiency of a low-speed working condition is improved. The power of the hydraulic speed regulating circuit and the power of the mechanical circuit are combined, and the hydraulic circuit only transmits partial power, so that high transmission efficiency and stepless speed regulation are realized. Compared with a hydraulic mechanical power gear shifting gearbox of the loader, the invention can greatly improve the transmission efficiency of the transmission device, ensure that the engine always works in an economic rotating speed range and reduce the oil consumption and the noise level of the loader.
The stepless transmission device comprises: the planetary speed regulation mechanism comprises a hydraulic speed regulation loop, a planetary distributing and converging mechanism, a first-section fixed shaft gear transmission mechanism of hydraulic machinery, a second-section fixed shaft gear transmission mechanism of the hydraulic machinery, a third-section fixed shaft gear transmission mechanism of the hydraulic machinery and a reverse gear mechanism.
the input shaft 5 is fixedly connected with a gear S4, and the other end of the input shaft 5 is a power take-off port PTO 2. Gear S4 is engaged with gear R41, which is attached to shaft a 37; one end of the shaft a37 is connected to the hydraulic pump 2, and the other end is a power take-off port PTO1, which can transfer the power of the engine to a hydraulic governor circuit. Meanwhile, the gear S4 is also meshed with the gear C8 in the planetary distributing and collecting mechanism, and the power of the engine is transmitted to the planetary distributing and collecting mechanism.
The hydraulic speed regulation loop comprises: a hydraulic pump 2, a hydraulic motor 11 and an oil replenishment pump 3; the hydraulic pump 2 is a bidirectional variable pump, the hydraulic motor 11 is a fixed displacement motor, the hydraulic pump 2 and the hydraulic motor 11 form a closed hydraulic loop, the oil replenishing pump 3 which is connected with the hydraulic pump 2 on the shaft A37 maintains the low pressure of the closed loop, and provides control oil pressure for the variable hydraulic pump 2. Part of the power from the engine enters a hydraulic circuit through the hydraulic pump 2 and the oil supplementing pump 3 to convert mechanical energy into hydraulic energy, and then enters a branch and confluence mechanism through a gear D13 connected to a power output shaft of the hydraulic motor 11 to be subjected to power confluence.
the planet distributing and converging mechanism consists of three planet rows, wherein a gear C8, a first planet row gear ring 12 and a third planet row planet carrier 39 are coaxially and fixedly connected on a shaft B42, and a gear C8 is meshed with a gear S4; the first planet row planet carrier 10, the third planet row gear ring 40, the second planet row planet carrier 31 and a gear A6 which is sleeved on a shaft B42 in an empty mode are fixedly connected; the third planet row sun gear 38, the second planet row sun gear 32 and the gear P34 which are sleeved on the shaft B42 in an empty mode are fixedly connected; the gear B7 which is sleeved on the shaft B42 in an empty way is fixedly connected with the first planet row sun gear 9 which is sleeved on the shaft B42 in an empty way, and the gear B7 is meshed with the gear D13; the second planet row ring gear 30 is fixedly connected with a gear Q35 which is freely sleeved on the shaft B42. Mechanical power from the engine is input into the planetary branch and confluence mechanism from the gear C8, hydraulic power from the hydraulic circuit is meshed with the gear B7 through the gear D13 and is input into the planetary branch and confluence mechanism, and the two parts of power are coupled in the branch and confluence mechanism. The gear Q35 is output from section I of the hydraulic machine, the gear P34 is output from section II of the hydraulic machine, and the gear A6 is output from section III of the hydraulic machine.
I section dead axle gear drive of hydraulic machinery includes: gear M26, clutch KV129, gear E14, gear H17, and gear J20. The gear M26 is meshed with a gear Q35 of the planetary distributing and converging mechanism, the gear M26 is connected with the driving end of a clutch KV129, the driven end of the clutch KV129 is fixedly connected with a gear E14, the gear E14 is meshed with a gear H17, the gear H17 is meshed with a gear J20, and the gear J20 is fixedly connected to the output shaft 21. When the clutch KV129 is engaged, power from the planetary splitting and converging mechanism is input from the gear M26 to the first-stage fixed-axis gear transmission mechanism of the hydraulic machine, and then transmitted to the output shaft 21 via the gear M26, the clutch KV129, the gear E14, the gear H17, and the gear J20 in this order, and output from the output shaft 21.
the II sections of dead axle gear drive mechanisms of hydraulic machinery include: gear N27, clutch KV228, gear E14, gear H17, and gear J20. The gear N27 is meshed with a gear P34 in the planet distributing and converging mechanism, the gear N27 is connected with the driving end of the clutch KV228, the driven end of the clutch KV228 is fixedly connected with a gear E14, the gear E14 is meshed with a gear H17, the gear H17 is meshed with a gear J20, and the gear J20 is fixedly connected to the output shaft 21. When the clutch KV228 is engaged, the power from the planetary splitting and converging mechanism is input from the gear N27 to the second-stage fixed-axis gear transmission mechanism of the hydraulic machine, and then transmitted to the output shaft 21 through the gear N27, the clutch KV228, the gear E14, the gear H17, and the gear J20 in this order, and is output from the output shaft 21.
III sections dead axle gear drive of hydraulic machinery includes: the gear comprises a gear G16, a gear I19, a clutch KV318, a gear H17 and a gear J20. The gear G16 is meshed with the gear A6 of the planet distributing and converging mechanism and is meshed with the gear I19, the gear I19 is connected with the driven end of the clutch KV318, the driving end of the clutch KV318 is fixedly connected with the gear H17, the gear H17 is meshed with the gear J20, and the gear J20 is fixedly connected to the output shaft 21. When the clutch KV318 is engaged, the power from the planetary splitting and merging mechanism is input from the gear G16 to the hydraulic machine iii-stage fixed-axis gear transmission mechanism, and then transmitted to the output shaft 21 via the gear G16, the gear I19, the clutch KV318, the gear H17, and the gear J20 in this order, and is output from the output shaft 21.
reverse gear mechanism includes: gear K22, reverse clutch KR125, gear L23, reverse clutch KR224, and gear F15. The gear K22 and the gear L23 are coaxially and idly sleeved on a gear shaft of the gear F15, the gear K22 is meshed with a gear M26 in a first-section fixed-axis gear transmission mechanism of the hydraulic machine, the gear L23 is meshed with a gear N27 in a second-section fixed-axis gear transmission mechanism of the hydraulic machine, and the gear F15 is meshed with a gear H17. The driving end of the reverse clutch KR125 is connected with the gear K22, and the driven end is fixedly connected with the gear shaft of the gear F15; the driving end of the reverse clutch KR224 is connected with the gear L23, and the driven end is fixedly connected with the gear shaft of the gear F15.
The engine power is input from the input shaft 5, passes through the continuously variable transmission, and is output to the front and rear axles of the loader. In the transmission device, except a planet separating and converging mechanism, other parts adopt fixed-shaft gear transmission, and shafts in the transmission device are all supported on a shell 1.
The forward gear of the stepless transmission device comprises three hydraulic mechanical sections which are respectively used for starting, low-speed operation and high-speed walking, and the reverse gear comprises two hydraulic mechanical sections; the specific implementation mode is as follows:
The first section is hydraulic machinery I section: under the working condition, the clutch KV129 is connected, and the rest clutches are disconnected; the power from the planetary distributing and converging mechanism is input into the I-section fixed-axis gear transmission mechanism of the hydraulic machine from the gear M26, then is transmitted to the output shaft 21 through the gear M26, the clutch KV129, the gear E14, the gear H17 and the gear J20 in sequence, and is output from the output shaft 21.
the second section is a hydraulic machine II section: under the working condition, the clutch KV228 is connected, and the rest clutches are disconnected; the power from the planetary distributing and converging mechanism is input into the hydraulic machine II-stage fixed-axis gear transmission mechanism from the gear N27, and then is transmitted to the output shaft 21 through the gear N27, the clutch KV228, the gear E14, the gear H17 and the gear J20 in sequence, and is output from the output shaft 21.
The third section is a hydraulic machine III section: under this condition, the KV318 clutch is engaged, and the rest clutches are disconnected; the power from the planetary distributing and converging mechanism is input into the third-stage fixed-axis gear transmission mechanism of the hydraulic machine from the gear G16, and then is transmitted to the output shaft 21 through the gear G16, the gear I19, the clutch KV318, the gear H17 and the gear J20 in sequence, and is output from the output shaft 21.
Reverse gear hydraulic machinery I section: in this condition, the reverse clutch KR125 is engaged and the remaining clutches are disengaged; the power from the planetary branch and confluence mechanism is input to the reverse gear mechanism through the gear M26, sequentially transmitted to the output shaft 21 through the gear M26, the gear K22, the reverse clutch KR125, the gear F15, the gear H17 and the gear J20, and output from the output shaft 21.
and a reverse gear hydraulic machine II section: in this condition, reverse clutch KR224 is engaged and the remaining clutches are disengaged; the power from the planetary power splitting and combining mechanism is input to the reverse mechanism through the gear N27, and is transmitted to the output shaft 21 through the gear N27, the gear L23, the reverse clutch KR224, the gear F15, the gear H17, and the gear J20 in this order, and is output from the output shaft 21.
the transmission segment change logic is shown in table 1.
TABLE 1 three-segment hydromechanical segment-change logic
The transmission device can realize power gear shifting, when the gear shifting sections are connected, only one clutch needs to be operated, the clutch at the next section can be engaged firstly, and then the clutch at the previous section is separated, so that uninterrupted power transmission is realized, uninterrupted power transmission is ensured, the operation efficiency is improved, and the gear shifting comfort is ensured.
The transmission has two power take-offs, PTO1 and PTO2 shown in fig. 1, connecting shaft a37 and input shaft 5, respectively.
The transmission device adopts a planetary mechanism to converge hydraulic power and mechanical power and is formed by connecting three hydraulic mechanical sections in a torque-dividing, speed-converging and power-dividing mode. The first section of the hydraulic machine is used for starting, the second section of the hydraulic machine is used for low-speed operation working conditions, and the third section of the hydraulic machine is used for high-speed walking. The hydraulic power and the mechanical power are combined, so that the transmission efficiency is higher than that of a hydraulic mechanical power shift gearbox; can ensure high transmission efficiency and low oil consumption in the operation and transition processes. The working condition of backing a car is two sections, namely a reverse hydraulic machine I section and a reverse hydraulic machine II section.
In summary, the above description is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (5)
1. Loader hydraulic pressure machinery stepless transmission, its characterized in that includes: the speed-regulating planetary transmission mechanism comprises a hydraulic speed-regulating loop, a planetary distributing and converging mechanism, a first-section fixed shaft gear transmission mechanism of hydraulic machinery, a second-section fixed shaft gear transmission mechanism of the hydraulic machinery, a third-section fixed shaft gear transmission mechanism of the hydraulic machinery and a reverse gear mechanism;
The hydraulic speed regulation loop comprises: a closed hydraulic circuit consisting of a hydraulic pump (2) and a hydraulic motor (11); the hydraulic pump (2) is connected with a shaft A (37) fixedly connected with a gear R (41); the gear R (41) is meshed with a gear S (4) fixedly connected to the input shaft (5); after the power of the engine is input from the input shaft (5), one part of the power enters a closed hydraulic loop through the hydraulic pump (2) to convert mechanical energy into hydraulic energy, and then enters a branch and confluence mechanism through a gear D (13) connected to a power output shaft of the hydraulic motor (11) to be subjected to power confluence;
the planet distributing and converging mechanism comprises three planet rows, a gear A (6), a gear B (7), a gear C (8), a gear P (34) and a gear Q (35); the gear C (8), the first planet row gear ring (12) and the third planet row planet carrier (39) are coaxially and fixedly connected, and the gear C (8) is meshed with the gear S (4); the first planet row planet carrier (10), the third planet row gear ring (40), the second planet row planet carrier (31) and the gear A (6) are fixedly connected; the third planet row sun gear (38), the second planet row sun gear (32) and the gear P (34) are fixedly connected; a gear B (7) meshed with the gear D (13) is fixedly connected with a first planet row sun gear (9); the second planet row gear ring (30) is fixedly connected with the gear Q (35);
I section dead axle gear drive of hydraulic machinery includes: a gear M (26) meshed with a gear Q (35) in the planetary distributing and converging mechanism, a gear E (14) connected with the gear M (26) through a clutch KV1(29), and a gear H (17) meshed with the gear E (14);
II sections dead axle gear drive of hydraulic machinery include: a gear N (27) meshed with a gear P (34) in the planetary distributing and converging mechanism, a gear E (14) connected with the gear N (27) through a clutch KV2(28), and a gear H (17) meshed with the gear E (14);
III sections dead axle gear drive of hydraulic machinery includes: a gear G (16) meshed with a gear A (6) in the planetary distributing and converging mechanism, a gear I (19) meshed with the gear G (16), and a gear H (17) connected with the gear I (19) through a clutch KV3 (18);
The gear H (17) is meshed with a gear J (20) fixedly connected to an output shaft (21);
The reverse gear mechanism comprises: a gear K (22) meshing with the gear M (26), a gear L (23) meshing with the gear N (27), and a gear F (15) meshing with the gear H (17); the gear K (22) is connected with the gear F (15) through a reverse clutch KR1(25), and the gear L (23) is connected with the gear F (15) through a reverse clutch KR2 (24).
2. The loader hydro-mechanical stepless transmission as set forth in claim 1, characterized in that said hydraulic governor circuit further comprises: and the oil replenishing pump (3) maintains the low-pressure of the closed hydraulic loop and provides control oil pressure for the hydraulic pump (2).
3. The loader hydromechanical continuously variable transmission as claimed in claim 1 or 2, characterized in that the forward gear of the continuously variable transmission comprises three hydromechanical sections for starting, low-speed operation and high-speed travel, respectively;
For launch, the clutch KV1(29) is engaged; mechanical power entering the planetary distributing and converging mechanism from the gear C (8) and hydraulic power entering the planetary distributing and converging mechanism from the gear B (7) are merged in the planetary distributing and converging mechanism, output from the gear Q (35), and then sequentially transmitted to an output shaft (21) through the gear M (26), the clutch KV1(29), the gear E (14), the gear H (17) and the gear J (20);
for low speed operation, the clutch KV2(28) is engaged; mechanical power entering the planetary distributing and converging mechanism from the gear C (8) and hydraulic power entering the planetary distributing and converging mechanism from the gear B (7) are merged in the planetary distributing and converging mechanism, output from the gear P (34), and then sequentially transmitted to an output shaft (21) through the gear N (27), the clutch KV2(28), the gear E (14), the gear H (17) and the gear J (20);
For high speed travel, the clutch KV3(18) is engaged; the mechanical power entering the planetary splitting and merging mechanism from the gear C (8) and the hydraulic power entering the planetary splitting and merging mechanism from the gear B (7) are merged in the planetary splitting and merging mechanism, output from the gear a (6), and then transmitted to the output shaft (21) through the gear G (16), the gear I (19), the clutch KV3(18), the gear H (17), and the gear J (20) in this order.
4. The loader hydro-mechanical continuously variable transmission as defined in claim 1 or 2, characterized in that it has two reverse-gear hydro-mechanical sections:
When the reverse gear clutch KR1(25) When the clutch is engaged, the stepless transmission device is positioned at the I section of the reverse hydraulic machine; to comeThe power from the planet branch and confluence mechanism is input into a reverse gear mechanism through the gear M (26) and then sequentially passes through the gear K (22) and the reverse gear clutch KR1(25) The gear F (15), the gear H (17) and the gear J (20) are transmitted to an output shaft (21);
when the reverse gear clutch KR2(24) when the clutch is engaged, the stepless transmission device is positioned in a reverse gear hydraulic machine II section: the power from the planetary distributing and converging mechanism is input into a reverse gear mechanism through the gear N (27), and then sequentially passes through the gear L (23) and the reverse gear clutch KR2(24) The gear F (15), the gear H (17) and the gear J (20) are transmitted to an output shaft (21).
5. The loader hydromechanical continuously variable transmission as claimed in claim 1 or 2, characterized in that the shaft a (37) and the input shaft (5) are provided with power take-off ports.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710299575.1A CN107246467B (en) | 2017-05-02 | 2017-05-02 | Stepless transmission device for hydraulic machinery of loader |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710299575.1A CN107246467B (en) | 2017-05-02 | 2017-05-02 | Stepless transmission device for hydraulic machinery of loader |
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| Publication Number | Publication Date |
|---|---|
| CN107246467A CN107246467A (en) | 2017-10-13 |
| CN107246467B true CN107246467B (en) | 2019-12-13 |
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| CN201710299575.1A Active CN107246467B (en) | 2017-05-02 | 2017-05-02 | Stepless transmission device for hydraulic machinery of loader |
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| WO2019195992A1 (en) * | 2018-04-10 | 2019-10-17 | 北京理工大学 | Three-section mechanical composite stepless transmission apparatus for use in engineering machinery |
| CN110397732A (en) * | 2019-08-02 | 2019-11-01 | 合肥工业大学 | A kind of dynamic property speed change optimal control method considering HMT transmission efficiency |
| CN113090731A (en) * | 2021-03-23 | 2021-07-09 | 北京理工大学 | Multi-power flow composite stepless transmission device |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102943859A (en) * | 2012-11-23 | 2013-02-27 | 天津工程机械研究院 | Hydraulic mechanical continuously variable transmission for loader |
| CN103453104A (en) * | 2013-07-22 | 2013-12-18 | 北京理工大学 | Four-segment hydraulic mechanical composite transmission device |
| RU2013124307A (en) * | 2013-05-28 | 2014-12-10 | Евгений Владимирович Габай | TRANSMISSION WITH HYDRAULIC INTER-axle and inter-wheel DIFFERENTIAL RELATIONS AND AUTOMATIC CONTROL OF THE MODES OF THEIR LOCKING FOR THE WHEELED VEHICLE |
| CN204300275U (en) * | 2014-10-28 | 2015-04-29 | 吉林大学 | Hydraulic pressure and the two speed change regulated of servomotor input constant speed output device |
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| JP2005096518A (en) * | 2003-09-22 | 2005-04-14 | Kanzaki Kokyukoki Mfg Co Ltd | Propeller shaft driving device for ship |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102943859A (en) * | 2012-11-23 | 2013-02-27 | 天津工程机械研究院 | Hydraulic mechanical continuously variable transmission for loader |
| RU2013124307A (en) * | 2013-05-28 | 2014-12-10 | Евгений Владимирович Габай | TRANSMISSION WITH HYDRAULIC INTER-axle and inter-wheel DIFFERENTIAL RELATIONS AND AUTOMATIC CONTROL OF THE MODES OF THEIR LOCKING FOR THE WHEELED VEHICLE |
| CN103453104A (en) * | 2013-07-22 | 2013-12-18 | 北京理工大学 | Four-segment hydraulic mechanical composite transmission device |
| CN204300275U (en) * | 2014-10-28 | 2015-04-29 | 吉林大学 | Hydraulic pressure and the two speed change regulated of servomotor input constant speed output device |
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