CN112377592A - Single-stage planetary gear return flow type hydraulic mechanical stepless transmission system - Google Patents

Single-stage planetary gear return flow type hydraulic mechanical stepless transmission system Download PDF

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CN112377592A
CN112377592A CN202011279654.4A CN202011279654A CN112377592A CN 112377592 A CN112377592 A CN 112377592A CN 202011279654 A CN202011279654 A CN 202011279654A CN 112377592 A CN112377592 A CN 112377592A
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gear
power
planetary gear
hydraulic
transmission system
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孙冬野
夏宇
胡明辉
胡建军
吴卓航
姜海飞
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Chongqing University
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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
    • F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
    • F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
    • 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
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses a single-stage planetary gear backflow type hydraulic mechanical stepless transmission system which comprises a power input device, a planetary row, a hydraulic backflow device and a power output device, wherein the power input device comprises an input shaft driven by an engine, the hydraulic backflow device comprises a variable pump and a hydraulic quantitative motor, and the planetary row comprises a planetary frame, a sun gear, a planetary gear and a gear ring which are mutually matched. By adopting the single-stage planetary gear return flow type hydraulic mechanical stepless transmission system provided by the invention, the single-stage planetary gear return flow type hydraulic mechanical stepless transmission system has more advantages in the aspects of torque characteristics and efficiency characteristics, and meanwhile, the return flow transmission speed ratio has wider variation range and larger torque ratio.

Description

Single-stage planetary gear return flow type hydraulic mechanical stepless transmission system
Technical Field
The invention relates to the technical field of mechanical transmission, in particular to a single-stage planetary gear return flow type hydraulic mechanical stepless transmission system.
Background
The Continuously Variable Transmission (CVT) is an ideal transmission form recognized by the world, and can enable the vehicle to work in an ideal working area all the time, so that the economy of the vehicle is greatly improved. Compared with mechanical transmission with a step gear, the stepless speed change transmission has a wider speed ratio change range, so that the adaptability of the vehicle to different working environments is more excellent.
Hydraulic stepless transmissions, represented by hydraulic pump-motors, are receiving much attention because of the small size, light weight of hydraulic components and the outstanding advantages over other forms of stepless transmissions (mechanical friction, hydraulic, electric). However, the conventional hydraulic stepless transmission represented by a hydraulic pump-motor has problems of lower transmission efficiency and higher cost than the stepped mechanical transmission.
The traditional tandem hydraulic stepless speed change transmission structure consists of an engine, a hydraulic pump-motor and a gear speed change device. Although this configuration allows for stepless speed change, it is not ideal because all of the power of the system goes through the low efficiency components (hydraulic pump-motor), resulting in overall inefficiency.
The present parallel hydraulic mechanical stepless speed change transmission structure commonly used in engineering special vehicles and agricultural vehicles consists of an engine, a hydraulic pump-motor, a gear speed change device and a planet row. But due to the structural design problem, the defects of low overall efficiency and non-ideal work also exist.
Disclosure of Invention
In order to solve the technical problems, the invention provides a single-stage planetary gear return flow type hydraulic mechanical stepless transmission system.
The technical scheme is as follows:
a single-stage planetary gear backflow type hydraulic mechanical stepless transmission system is characterized by comprising a power input device, a planetary row, a hydraulic backflow device and a power output device, wherein the power input device comprises an input shaft driven by an engine, the hydraulic backflow device comprises a variable pump and a hydraulic quantitative motor, and the planetary row comprises a planetary frame, a sun gear, a planetary gear and a gear ring which are matched with each other;
the output power of the input shaft is transmitted to the planet wheel through the planet carrier, and the planet wheel transmits part of the power to the power output device through the gear ring and the power output device outputs the power outwards;
the planet wheel transmits the rest power to the sun wheel, the variable pump and the hydraulic quantitative motor in sequence, then transmits the power back to the input shaft, and is coupled with the power output by the engine to the input shaft;
and the power transmitted by the planet wheel to the power output device is larger than the power transmitted by the planet wheel to the variable pump.
By adopting the structure, most of input power output by the engine to the input shaft is transmitted to the power output device through the planet carrier, the planet wheel and the gear ring to form a mechanical transmission path; a small part of power is sequentially transmitted to a sun gear, a variable pump and a hydraulic quantitative motor through a planet gear and then flows back to an input shaft for power coupling to form a hydraulic transmission backflow path; through two power transmission paths, power loss is greatly reduced, and meanwhile, the whole system obtains the effect of low-speed torque increase by utilizing the characteristic of a hydraulic transmission backflow path.
Preferably, the method comprises the following steps: the planet carrier is connected on the input shaft in a synchronous rotating mode, the input shaft is connected with the hydraulic quantitative motor after penetrating through the variable pump, the hydraulic quantitative motor is connected with the variable pump, and the variable pump is connected with the sun gear. By adopting the structure, two-path transmission can be stably and reliably carried out.
Preferably, the method comprises the following steps: the variable pump is provided with a central sleeve for inputting power, the sun gear is connected to the central sleeve in a synchronous rotating mode, and the input shaft penetrates through the central sleeve and then is connected with the hydraulic quantitative motor. By adopting the structure, the structure is more compact while the stable and reliable transmission can be ensured.
Preferably, the method comprises the following steps: the gear shifting device is arranged between the gear ring and the power output device, between the planet carrier and the planet wheel, or between the sun wheel and the variable pump. By adopting the structure, the positions of the gear speed changing devices can be flexibly arranged according to actual requirements; when the actual working condition of the vehicle type is more pursuing large torque output to do work, the gear speed change device can be arranged between the planet carrier and the planet wheel; when the vehicle is more focused on the work efficiency, the gear shifting device may be disposed between the ring gear and the power output device.
Preferably, the method comprises the following steps: the gear speed change device comprises a speed change driving gear and a speed change driven gear, wherein the speed change driving gear and the speed change driven gear are synchronously rotated with the gear ring, and the speed change driven gear is meshed with the speed change driving gear and can transmit power to the power output device through the clutch. By adopting the structure, the gear speed change device is arranged between the gear ring and the power output device, so that the power loss in the transmission process is reduced, and the transmission efficiency is improved.
Preferably, the method comprises the following steps: the speed change driving gear and the gear ring are integrally formed. By adopting the structure, the structure has high structural strength, stability and reliability, and simultaneously reduces parts and cost.
Preferably, the method comprises the following steps: the power output device comprises an output shaft, and the output shaft is driven by the clutch. By adopting the structure, the power output is stably and reliably ensured.
Compared with the prior art, the invention has the beneficial effects that:
1. compared with the existing backflow type hydraulic mechanical stepless transmission device, the single-stage planetary gear backflow type hydraulic mechanical stepless transmission system has more advantages in the aspects of torque characteristics and efficiency characteristics, and the characteristic of low-speed torque increase has important application value for vehicle types such as engineering special vehicles, agricultural vehicles and the like;
2. compared with the existing flow-dividing transmission structure, the backflow transmission speed ratio of the single-stage planetary gear backflow type hydraulic mechanical stepless transmission system is wider in change range and larger in torque ratio (stronger in external acting capacity), although the efficiency and the flow-dividing transmission are slightly different, the efficiency difference of the backflow transmission speed ratio and the torque ratio can be reduced and even the efficiency of the backflow transmission speed ratio and the torque ratio is equal through the structural characteristics and the controllability of a variable pump-motor.
Drawings
FIG. 1 is a schematic diagram of the present invention;
FIG. 2 is a schematic diagram of the operation of the present invention;
FIG. 3 is a schematic view of the closed planetary transmission;
FIG. 4 is a graph of the basic characteristics of the present invention;
FIG. 5 is a schematic diagram of the gear shifting device disposed between the planetary gear and the power take off;
FIG. 6 is a schematic diagram of a range transmission disposed between a planet carrier and planet gears;
FIG. 7 is a schematic diagram of a range transmission disposed between a sun gear and a variable displacement pump.
Detailed Description
The present invention will be further described with reference to the following examples and the accompanying drawings.
As shown in fig. 1 and fig. 2, a single-stage planetary gear return flow type hydraulic mechanical stepless transmission system mainly comprises a power input device 1, a planetary row 3, a hydraulic return device 4 and a power output device 5, wherein the power input device 1 comprises an input shaft 1b driven by an engine 1a, the hydraulic return device 4 comprises a variable pump 4a and a hydraulic quantitative motor 4b, and the planetary row 3 comprises a planetary carrier 3a, a sun gear 3b, a planetary gear 3c and a gear ring 3d which are matched with each other.
The output power of the input shaft 1b is transmitted to the planet wheel 3c through the planet carrier 3a, the planet wheel 3c transmits part of the power to the power output device 5 through the gear ring 3d, and the power is output outwards by the power output device 5, and the transmission path forms a mechanical transmission path.
The planet wheel 3c transmits the rest power to the sun wheel 3b, the variable pump 4a and the hydraulic fixed-displacement motor 4b in sequence, then transmits the power back to the input shaft 1b, and is coupled with the power output by the engine 1a to the input shaft 1b, and the transmission path is a hydraulic transmission return path.
The power transmitted by the planetary gear 3c to the power output device 5 is larger than the power transmitted by the planetary gear 3c to the variable displacement pump 4 a. That is, most of the power is transmitted through the mechanical transmission path, and a small part of the power is coupled to the input shaft 1b through the hydraulic transmission backflow path in a backflow mode, so that the power loss is greatly reduced, and meanwhile, the whole system obtains the effect of low-speed torque increase by utilizing the characteristic of the hydraulic transmission backflow path.
Referring to fig. 2, a planet carrier 3a is connected to an input shaft 1b in a synchronous rotation manner, the input shaft 1b is connected to a hydraulic constant displacement motor 4b after passing through a variable displacement pump 4a, the hydraulic constant displacement motor 4b is connected to the variable displacement pump 4a, and the variable displacement pump 4a is connected to a sun gear 3 b. Specifically, the variable pump 4a is provided with a central sleeve 4c for inputting power, the sun gear 3b is connected to the central sleeve 4c in a synchronous rotating mode, the input shaft 1b penetrates through the central sleeve 4c and then is connected with the hydraulic quantitative motor 4b, a hydraulic transmission backflow path can be stably and reliably realized in transmission, and the structure is compact.
Referring to fig. 5-7, the single-stage planetary gear return type hydromechanical continuously variable transmission system further includes a gear shift device 2 (i.e., disposed at the power take-off), and the gear shift device 2 is disposed either between the ring gear 3d and the power take-off 5 (i.e., disposed in the mechanical transmission path), between the carrier 3a and the planetary gears 3c, or between the sun gear 3b and the variable pump 4a (i.e., disposed in the hydraulic transmission return path).
Through the design, the position of the gear speed change device 2 can be flexibly arranged according to actual requirements; when the actual working condition of the vehicle type is more pursuing large torque output to do work, the gear speed change device 2 can be arranged between the planet carrier 3a and the planet wheel 3 c; when the vehicle is more focused on the work efficiency, the gear shift device 2 may be disposed between the ring gear 3d and the power output device 5.
The embodiment takes the example that the gear speed change device 2 is arranged at the power output end as follows:
referring to fig. 2 and 3, the gear shift speed change device 2 includes a speed change driving gear 2a rotating in synchronization with the ring gear 3d and a speed change driven gear 2b engaged with the speed change driving gear 2a, and the speed change driven gear 2b can transmit power to the power output device 5 through a clutch 2 c. Wherein the speed change drive gear 2a is integrally formed with the ring gear 3 d. The power output device 5 includes an output shaft 5a, and the output shaft 5a is driven by the clutch 2 c.
The basic characteristics of a single-stage planetary gear return type hydromechanical stepless transmission system are explained as follows:
1. speed characteristics:
for the single planet row has the characteristics:
Figure BDA0002780348450000051
in the formula (1), ns、ncAnd nrThe rotation speeds of the sun gear, the planet carrier and the gear ring are respectively represented; k is a planet row structure parameter; ms、MrAnd McRepresenting the torque of the sun gear, the planet carrier and the ring gear respectively; ps、PrAnd PcRepresenting the transmitted power of the sun gear, the carrier and the ring gear, respectively.
Power passes through the planet row, then:
ns+knr-(1+k)nc＝0 (2)
wherein n isi＝nc＝nm，ns＝np，
Figure BDA0002780348450000052
The following can be obtained:
Figure BDA0002780348450000053
in the formulae (2) and (3), isysTo the transmission ratio, niAnd noThe rotational speeds of the input shaft 1b and the output shaft 5a, ibxIs the speed ratio of the x gear of the gear speed change device 2, epsilon is the displacement ratio of the hydraulic backflow device 4, k is the structural parameter of the planet row, and nmAnd npRespectively representing the rotating speeds of the fixed-quantity motor and the variable-quantity pump; i.e. iyRepresenting the speed ratio of the hydraulic system.
2. Moment characteristic:
the torque which can be transmitted by hydraulic transmission is limited not only by the slipping of friction links such as clutches, but also by the maximum oil pressure determined by a high-pressure overflow valve, namely peak pressure. Along with the increase of the external load, the working pressure of the system is increased, and the torque M of the output shaftoIncreasing the torque M of the output of the hydraulic constant displacement motor 4bmAnd also increases. When the output torque of the hydraulic constant-displacement motor 4b reaches the maximum value MmmaxWhen the hydraulic system is used, redundant pressure is unloaded through the overflow valve, and the output slipping phenomenon occurs. Therefore, the maximum output torque M of the reverse flow type hydraulic mechanical stepless transmissionomaxDependent on the maximum output torque M of the hydraulic motormmaxUsually with Mo/MmTo represent the torque characteristics of the system.
The planet row comprises:
Ms:Mr:Mc＝1:k:-(1+k) (4)
input torque MiAnd output torque MoThe relationship is as follows:
Figure BDA0002780348450000061
the following steps are provided:
Figure BDA0002780348450000062
in the transmission system, there are: mp＝Ms，
Figure BDA0002780348450000063
Wherein etayFor the efficiency of the hydraulic return device 4, therefore:
Figure BDA0002780348450000064
the torque coefficient in vehicle transmission is used as an important parameter index of torque characteristic, and is commonly used
Figure BDA0002780348450000065
The method can more intuitively obtain the relation between the input torque and the output torque of the transmission system, thereby well evaluating the external work-doing capability of the vehicle transmission system.
The planet row comprises:
Ms:Mr:Mc＝1:k:-(1+k) (8)
Figure BDA0002780348450000066
in the formula (9), etabxIndicating the efficiency of the x-th gear of the gear shifting device 2.
Because: mi+Mm+Mc1＝0 (10)
Therefore, the method comprises the following steps:
Figure BDA0002780348450000067
3. power splitting characteristics:
in a transmission system, power distribution proportion in a transmission path is often embodied by using a power splitting characteristic, so that the design is adjusted to improve the system efficiency, and the power splitting characteristic is generally used
Figure BDA0002780348450000071
To represent PmIs the output power of the motor, PoThe output power of the system.
The planet row comprises:
ns+knr-(1+k)nc＝0 (12)
Ms:Mr:Mc＝1:k:-(1+k) (13)
Pm＝Ps·ηy＝nsMs·ηy (14)
Po＝Pr·ηb1＝nrMr·ηb1 (15)
therefore, the method comprises the following steps:
Figure BDA0002780348450000072
4. efficiency characteristics:
if the efficiency loss of the rigid connection of the propeller shaft is assumed to be 0, the components in the system of the present invention that need to take into account the efficiency loss are: gear shift 2, hydraulic pressure reflux unit 4, planet row 3. The gear change-speed gearing 2 is generally a gearing formed by a gear-mesh pair, with a single-stage external-mesh-pair transmission efficiency eta being possiblebx＝0.97。ηyFor the efficiency of the hydraulic return device 4, the efficiency of the hydraulic elements is determined by the rotation speed, the displacement and the pressure, and can be obtained by fitting a test curve into a functional form.
In the transmission system, because the connection modes of the planetary rows 3 are various, the transmission efficiency is greatly different, and therefore the efficiency loss of the planetary rows in the transmission system cannot be ignored. The reverse flow transmission satisfies the C-I closed planetary transmission structure (see FIG. 3), so the efficiency of the reverse flow transmission is calculated as follows:
for the planet row, a, b, I and C respectively represent a sun gear, a planet carrier, an input shaft and an output shaft (gear ring) of the transmission system:
Figure BDA0002780348450000073
Figure BDA0002780348450000074
ψxrepresenting the loss coefficient of a-b-C when the planet carrier is fixed, according to the calculation psix＝0.024，ψal、ψbI、ηb、ηib1The loss coefficients of the paths a to I, the loss coefficients of the paths b to I, the transmission efficiency of the paths b to I and the transmission efficiency of the gear speed change device are respectively expressed.
The basic characteristic curve of the present invention is shown in fig. 4.
Finally, it should be noted that the above-mentioned description is only a preferred embodiment of the present invention, and those skilled in the art can make various similar representations without departing from the spirit and scope of the present invention.

Claims (7)

1. The utility model provides a single-stage planetary gear backward flow formula hydraulic machinery stepless transmission system which characterized in that: the device comprises a power input device (1), a planet row (3), a hydraulic backflow device (4) and a power output device (5), wherein the power input device (1) comprises an input shaft (1b) driven by an engine (1a), the hydraulic backflow device (4) comprises a variable pump (4a) and a hydraulic quantitative motor (4b), and the planet row (3) comprises a planet carrier (3a), a sun gear (3b), a planet gear (3c) and a gear ring (3d) which are matched with each other;
the output power of the input shaft (1b) is transmitted to a planetary gear (3c) through a planet carrier (3a), and partial power of the planetary gear (3c) is transmitted to a power output device (5) through a gear ring (3d) and is output outwards by the power output device (5);
the planet wheel (3c) transmits the rest part of power to the sun wheel (3b), the variable pump (4a) and the hydraulic quantitative motor (4b) in sequence, then transmits the power back to the input shaft (1b), and is coupled with the power output by the engine (1a) to the input shaft (1 b);
the power transmitted by the planet wheel (3c) to the power output device (5) is larger than the power transmitted by the planet wheel (3c) to the variable pump (4 a).
2. The single stage planetary gear return-flow hydromechanical continuously variable transmission system of claim 1, wherein: the planet carrier (3a) is connected to the input shaft (1b) in a synchronous rotating mode, the input shaft (1b) penetrates through the variable pump (4a) and then is connected with the hydraulic quantitative motor (4b), the hydraulic quantitative motor (4b) is connected with the variable pump (4a), and the variable pump (4a) is connected with the sun gear (3 b).
3. The single stage planetary gear return-flow hydromechanical continuously variable transmission system of claim 2, wherein: the variable pump (4a) is provided with a central sleeve (4c) for inputting power, the sun gear (3b) is connected to the central sleeve (4c) in a synchronous rotating mode, and the input shaft (1b) penetrates through the central sleeve (4c) and then is connected with the hydraulic quantitative motor (4 b).
4. The single stage planetary gear return-flow hydromechanical continuously variable transmission system of claim 1, wherein: the gear shifting device (2) is arranged between the planetary gear (3c) and the power output device (5), between the planet carrier (3a) and the planetary gear (3c), or between the sun gear (3b) and the variable pump (4 a).
5. The single stage planetary gear return-flow hydromechanical continuously variable transmission system of claim 4, wherein: the gear speed change device (2) comprises a speed change driving gear (2a) and a speed change driven gear (2b), wherein the speed change driving gear (2a) rotates synchronously with the gear ring (3d), the speed change driven gear (2b) is meshed with the speed change driving gear (2a), and power can be transmitted to the power output device (5) through the clutch (2 c).
6. The single stage planetary gear return-flow hydromechanical continuously variable transmission system of claim 5, wherein: the speed change driving gear (2a) and the ring gear (3d) are integrally formed.
7. The single stage planetary gear return-flow hydromechanical continuously variable transmission system of claim 5, wherein: the power output device (5) comprises an output shaft (5a), and the output shaft (5a) is driven by the clutch (2 c).
CN202011279654.4A 2020-11-16 2020-11-16 Single-stage planetary gear return flow type hydraulic mechanical stepless transmission system Pending CN112377592A (en)

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