CN112377593A - Double-stage planetary gear return flow type hydraulic mechanical stepless transmission system - Google Patents
Double-stage planetary gear return flow type hydraulic mechanical stepless transmission system Download PDFInfo
- Publication number
- CN112377593A CN112377593A CN202011281448.7A CN202011281448A CN112377593A CN 112377593 A CN112377593 A CN 112377593A CN 202011281448 A CN202011281448 A CN 202011281448A CN 112377593 A CN112377593 A CN 112377593A
- Authority
- CN
- China
- Prior art keywords
- gear
- power
- planet
- hydraulic
- input shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 82
- 238000006073 displacement reaction Methods 0.000 claims description 19
- 230000001360 synchronised effect Effects 0.000 claims description 5
- 230000009977 dual effect Effects 0.000 claims 5
- 238000000034 method Methods 0.000 description 12
- 230000009347 mechanical transmission Effects 0.000 description 10
- 238000010586 diagram Methods 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 238000010992 reflux Methods 0.000 description 3
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- NAWXUBYGYWOOIX-SFHVURJKSA-N (2s)-2-[[4-[2-(2,4-diaminoquinazolin-6-yl)ethyl]benzoyl]amino]-4-methylidenepentanedioic acid Chemical compound C1=CC2=NC(N)=NC(N)=C2C=C1CCC1=CC=C(C(=O)N[C@@H](CC(=C)C(O)=O)C(O)=O)C=C1 NAWXUBYGYWOOIX-SFHVURJKSA-N 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
Images
Classifications
-
- 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
Abstract
The invention discloses a double-stage planetary gear backflow type hydraulic mechanical stepless transmission system which comprises a power input device, a gear speed change device, a planetary row combination, 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, the planetary row combination comprises a first planetary row consisting of a first planet carrier, a first sun gear, a first planet gear and a first gear ring and a second planetary row consisting of a second planet carrier, a second sun gear, a second planet gear and a second gear ring. By adopting the two-stage planetary gear return flow type hydraulic mechanical stepless transmission system provided by the invention, the two-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, and can realize forward and reverse stepless speed regulation with wide speed regulation range.
Description
Technical Field
The invention relates to the technical field of mechanical transmission, in particular to a two-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 two-stage planetary gear return flow type hydraulic mechanical stepless transmission system.
The technical scheme is as follows:
the double-stage planetary gear backflow type hydraulic mechanical stepless transmission system is characterized by comprising a power input device, a gear speed change device, a planetary row combination, 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, the planetary row combination comprises a first planetary row consisting of a first planet carrier, a first sun gear, a first planet gear and a first gear ring and a second planetary row consisting of a second planet carrier, a second sun gear, a second planet gear and a second gear ring;
when the displacement ratio epsilon of the hydraulic backflow device is larger than 0, the first planetary row is opened, and the second planetary row is closed; the output power of the input shaft is transmitted to a first planet wheel through a first planet carrier, part of the power is transmitted to a power output device through a first gear ring and a gear speed change device by the first planet wheel and is output outwards by the power output device, and the rest of the power is transmitted to a first sun gear, a variable pump and a hydraulic quantitative motor in sequence by the first planet wheel and then transmitted back to the input shaft to be coupled with the power output to the input shaft by an engine, wherein the power transmitted to the power output device by the first planet wheel is greater than the power transmitted to the variable pump by the first planet wheel;
when the displacement ratio epsilon of the hydraulic backflow device is less than 0, the first planetary row is locked, and the second planetary row is opened; the output power of the input shaft is transmitted to the second planet wheel sequentially through the first planet carrier, the first planet wheel and the second gear ring, partial power of the second planet wheel is transmitted to the power output device sequentially through the second planet carrier and the gear speed change device and is output outwards through the power output device, the second planet wheel transmits the rest power to the second sun wheel, the variable pump and the hydraulic quantitative motor sequentially and then transmits the rest power back to the input shaft, and the power output to the input shaft by the engine is coupled, wherein the power transmitted to the power output device by the second planet wheel is larger than the power transmitted to the variable pump by the second planet wheel.
By adopting the structure, forward and reverse stepless speed regulation can be realized aiming at vehicle transmission, and the speed regulation range is large; when the displacement ratio epsilon of the hydraulic backflow device is larger than 0, the first planetary row is opened, the second planetary row is closed, most of input power output by the engine to the input shaft is transmitted to the power output device through the first planet carrier, the first planetary wheel and the first gear ring to form a mechanical transmission path, and a small part of power is sequentially transmitted to the first sun wheel, the variable pump and the hydraulic quantitative motor through the first planetary wheel and then flows back to the input shaft to be subjected to power coupling, so that a hydraulic transmission backflow path is formed; when the displacement ratio epsilon of the hydraulic backflow device is less than 0, the first planetary row is locked, the second planetary row is opened, most of input power output by the engine to the input shaft is transmitted to the power output device through the first planetary carrier, the first planetary wheel, the second gear ring, the second planetary wheel and the second planetary carrier to form a mechanical transmission path, and a small part of power is transmitted to the second sun wheel, the variable pump and the hydraulic quantitative motor in sequence through the second planetary wheel and then flows back to the input shaft to be subjected to power coupling, so that a hydraulic transmission backflow path is formed; the forward and reverse stepless speed regulation forms two power transmission paths, so that the power loss is greatly reduced, and meanwhile, the whole system obtains the effect of low-speed torque increase by utilizing the characteristics of a hydraulic transmission backflow path.
Preferably, the method comprises the following steps: the one end input shaft of first planet carrier, the other end is connected with first planet wheel, the one end and the first planet wheel of second ring gear are connected, and the other end meshes with the second planet wheel, the one end and the second planet wheel of second planet carrier are connected, and the other end is connected with gear speed change gear, the input shaft passes behind the variable pump and is connected with hydraulic pressure ration motor, hydraulic pressure ration motor is connected with the variable pump, first sun gear and second sun gear all are connected with the variable pump. By adopting the structure, the forward and reverse stepless speed regulation can stably and reliably carry out two-way transmission.
Preferably, the method comprises the following steps: the variable pump is provided with a central sleeve for inputting power, the first sun gear and the second sun gear are 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 speed change device comprises a first speed change driving gear, a first speed change driven gear, a second speed change driving gear and a second speed change driven gear, wherein the first speed change driving gear is synchronously rotated with the first gear ring, the first speed change driven gear is meshed with the first speed change driving gear, the second speed change driving gear is synchronously rotated with the second planet carrier, the second speed change driven gear is meshed with the second speed change driving gear, the first speed change driven gear can transmit power to the power output device through the first clutch, and the second speed change driven gear can transmit power to the power output device through the second clutch. By adopting the structure, the gear speed change device is arranged in front of the power output device, so that the power loss in the transmission process is reduced, the transmission efficiency is improved, and meanwhile, reliable power path switching can be performed through the first clutch and the second clutch.
Preferably, the method comprises the following steps: the first variable-speed driving gear and the first gear ring are integrally formed, and the second variable-speed driving gear and the second planet carrier 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 take-off comprises an output shaft which can be driven by the first clutch or the second 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. the two-stage planetary gear return flow type hydraulic mechanical stepless transmission system can realize forward and reverse two-way stepless speed regulation, and has a large speed regulation range;
2. compared with the existing backflow type hydraulic mechanical stepless transmission device, the two-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;
3. compared with the existing flow-dividing transmission structure, the backflow transmission speed ratio of the double-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 power flow diagram of the system of the present invention for ε > 0;
FIG. 4 is a power flow diagram of the system of the present invention when ε < 0;
FIG. 5 is a schematic view of the closed planetary transmission configuration with ε > 0;
FIG. 6 is a schematic view of the closed planetary transmission configuration when ε < 0;
FIG. 7 is a graph of the basic characteristics of the present invention for ε > 0;
FIG. 8 is a graph of the basic characteristics of the present invention for ε < 0.
Detailed Description
The present invention will be further described with reference to the following examples and the accompanying drawings.
As shown in fig. 1-6, a double-stage planetary gear return type hydraulic mechanical stepless transmission system mainly includes a power input device 1, a gear speed changing device 2, a planetary row combination 3, a hydraulic return device 4 and a power output device 5, where the power input device 1 includes an input shaft 1b driven by an engine 1a, the hydraulic return device 4 includes a variable pump 4a and a hydraulic quantitative motor 4b, and the planetary row combination 3 includes a first planetary row composed of a first planet carrier 3a, a first sun gear 3b, a first planet gear 3c and a first ring gear 3d, and a second planetary row composed of a second planet carrier 3e, a second sun gear 3f, a second planet gear 3g and a second ring gear 3 h.
When the displacement ratio epsilon of the hydraulic reflux device 4 is larger than 0, the first planetary row is opened, and the second planetary row is closed (the first clutch 2c is in a combined state, and the second clutch 2f is in a disconnected state); the output power of the input shaft 1b is transmitted to the first planet wheel 3c through the first planet carrier 3a, the first planet wheel 3c transmits part of the power to the power output device 5 through the first gear ring 3d and the gear speed change device 2 in sequence, the power output device 5 outputs the power outwards, and the transmission path forms a mechanical transmission path; the first planetary gear 3c transmits the rest power to the first sun gear 3b, the variable pump 4a and the hydraulic fixed-displacement motor 4b in sequence, then transmits the rest 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 first planetary gear 3c to the power take-off 5 is greater than the power transmitted by the first 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.
When the displacement ratio epsilon of the hydraulic reflux device 4 is less than 0, the first planetary row is locked, and the second planetary row is opened (the first clutch 2c is in a disconnected state, and the second clutch 2f is in a combined state); the output power of the input shaft 1b is transmitted to the second planet gear 3g sequentially through the first planet carrier 3a, the first planet gear 3c and the second gear ring 3h, part of the power is transmitted to the power output device 5 sequentially through the second planet carrier 3e and the gear speed change device 2 by the second planet gear 3g, the power is output outwards by the power output device 5, and the transmission path forms a mechanical transmission path; the second planet wheel 3g transmits the rest power to the second sun wheel 3f, the variable pump 4a and the hydraulic fixed-displacement motor 4b in sequence, then transmits the rest 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 second planetary gear 3g to the power output device 5 is greater than the power transmitted by the second planetary gear 3g to the variable 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, one end of the first planet carrier 3a is connected to the input shaft 1b, the other end is connected to the first planet wheel 3c, one end of the second ring gear 3h is connected to the first planet wheel 3c, the other end is engaged with the second planet wheel 3g, one end of the second planet carrier 3e is connected to the second planet wheel 3g, the other end is connected to the gear shifting device 2, the input shaft 1b passes through the variable pump 4a and then is connected to the hydraulic constant displacement motor 4b, the hydraulic constant displacement motor 4b is connected to the variable pump 4a, and the first sun gear 3b and the second sun gear 3f are both connected to the variable pump 4 a.
The variable pump 4a is provided with a central sleeve 4c for inputting power, the first sun gear 3b and the second sun gear 3f are 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 guaranteed to be stably and reliably transmitted, and the structure is compact.
It is noted that the position of the gearshift transmission 2 can be flexibly arranged according to actual needs; 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 on a mechanical transmission path; when the vehicle is more focused on the work efficiency, the gear shifting device 2 may be disposed in front of the power output device 5.
The present embodiment takes as an example that the gear shift device 2 is provided before the power output device 5:
referring to fig. 2, the gear shift speed change device 2 includes a first speed change driving gear 2a rotating synchronously with the first ring gear 3d, a first speed change driven gear 2b engaged with the first speed change driving gear 2a, a second speed change driving gear 2d rotating synchronously with the second carrier 3e, and a second speed change driven gear 2e engaged with the second speed change driving gear 2d, wherein the first speed change driven gear 2b can transmit power to the power output device 5 through a first clutch 2c, and the second speed change driven gear 2e can transmit power to the power output device 5 through a second clutch 2 f. The first transmission driving gear 2a and the first ring gear 3d are integrally formed, and the second transmission driving gear 2d and the second carrier 3e are integrally formed. The power take-off 5 comprises an output shaft 5a, which output shaft 5a can be driven by the first clutch 2c or the second clutch 2 f.
The basic characteristics of a two-stage planetary gear return type hydromechanical stepless transmission system are explained as follows:
1. speed characteristics:
for the single planet row has the characteristics:
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 power transmitted by the sun gear, the planet carrier and the ring gear, respectively.
When ε > 0, the second planetary row is locked, power passes through the first planetary row, then:
ns1+k1nr1-(1+k1)nc1＝0 (2)
wherein n isi＝nc1＝nm，ns1＝np，
The following can be obtained:
similarly, when ε < 0, lock first planet row, power passes through second planet row, then:
ns2+k2nr2-(1+k2)nc2＝0 (4)
wherein n isi＝nr2＝nm，ns2＝np，
The following can be obtained:
in the formulae (2), (3), (4) and (5), isysTo the transmission ratio, niAnd noThe rotational speeds of the input shaft 1b and the output shaft 5a, ibxThe speed ratio of the x gear of the gear speed change device 2, epsilon is the displacement ratio of the hydraulic backflow device 4, and k1Is the first planet row structure parameter, k2Is a second planet row structural parameter, ns1、nc1、nr1、nmAnd npRespectively representing the rotating speeds of the first sun gear, the first planet carrier, the first gear ring, the hydraulic constant displacement motor and the variable displacement pump; i.e. iyRepresenting the hydraulic system speed ratio.
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.
When ε > 0, for the first row of stars:
Ms1:Mr1:Mc1＝1:k1:-(1+k1) (6)
in formula (6), Ms1、Mr1、Mc1Representing the torques of the first sun gear, the first planet carrier and the first ring gear, respectively.
Input torque MiAnd output torque MoThe relationship is as follows:
the following steps are provided:
in the transmission system, there are: mp＝Ms1，
ηyFor the efficiency of the hydraulic return device 4, therefore:
the same principle is that: when epsilon is less than 0, k is set for the second planetary row2Comprises the following steps:
Ms2:Mr2:Mc2＝1:k2:-(1+k2) (10)
in formula (10), Ms2、Mr2、Mc2Representing the torques of the second sun gear, the second carrier and the second ring gear, respectively.
Also, there are: mp＝Ms2，
Therefore, the method comprises the following steps:
the torque coefficient in vehicle transmission is used as an important parameter index of torque characteristic, and is commonly used
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.
When ε > 0, for the first row of stars:
Ms1:Mr1:Mc1＝1:k1:-(1+k1) (15)
in the formula (16), etabxRepresenting the gear change efficiency.
Because: mi+Mm+Mc1＝0； (17)
Therefore, the method comprises the following steps:
similarly, when ε < 0, for the second planet row there is:
Ms2:Mr2:Mc2＝1:k2:-(1+k2) (19)
also because: mi+Mm+Mr2＝0(21)
Therefore, the method comprises the following steps:
3. power splitting characteristics:
in transmission systems, power splitting features are often usedThe power distribution proportion in the transmission path is reflected, the design is adjusted to improve the system efficiency, and the method is generally used
To represent PmIs the output power of the motor, PoThe output power of the system.
When ε > 0, for the first row of stars:
ns1+k1nr1-(1+k1)nc1＝0 (23)
Ms1:Mr1:Mc1＝1:k1:-(1+k1) (24)
Pm＝Ps1·ηy＝ns1Ms1·ηy (25)
Po＝Pr1·ηb1＝nr1Mr1·ηb1 (26)
therefore, the method comprises the following steps:
similarly, when ε < 0, for the second planet row there is:
ns2+k2nr2-(1+k2)nc2＝0 (28)
Ms2:Mr2:Mc2＝1:k2:-(1+k2) (29)
Pm＝Ps2·ηy＝ns2Ms2·ηy (30)
Po＝Pc2·ηb2＝nc2Mc2·ηb2 (31)
therefore, the method comprises the following steps:
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 speed change device 2, hydraulic pressure reflux unit 4, planet row combination 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 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 configuration (see FIGS. 6 and 7), so the efficiency of the reverse flow transmission is calculated as follows:
when epsilon is more than 0, for the first planet row, a, b, I and C are taken to respectively represent a first sun gear, a first planet carrier, an input shaft and an output shaft (a first gear ring) of the transmission system:
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.
When epsilon is less than 0, for the second planet row, d, e, I and C are taken to respectively represent a second gear ring, a second sun gear, an input shaft and an output shaft (a second planet carrier) of the transmission system:
in the same way, #xRepresenting the loss factor of d-e-C,. psi, with the planet carrier fixedx＝0.024，ψdl、ψeI、ηe、ηib2And the loss coefficients of the d-I path, the loss coefficients of the e-I path, the transmission efficiency of the e-I path and the transmission efficiency of the gear speed change device are respectively expressed.
The basic characteristic curves of the present invention are shown in fig. 7 and 8.
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 (6)
1. The utility model provides a doublestage planetary gear backward flow formula hydraulic machinery stepless transmission system which characterized in that: the power transmission device comprises a power input device (1), a gear speed change device (2), a planet row combination (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), the planet row combination (3) comprises a first planet row consisting of a first planet carrier (3a), a first sun gear (3b), a first planet gear (3c) and a first gear ring (3d) and a second planet row consisting of a second planet carrier (3e), a second sun gear (3f), a second planet gear (3g) and a second gear ring (3 h);
when the displacement ratio epsilon of the hydraulic backflow device (4) is larger than 0, the first planetary row is opened, and the second planetary row is closed; the output power of the input shaft (1b) is transmitted to a first planet wheel (3c) through a first planet carrier (3a), part of the power of the first planet wheel (3c) is transmitted to a power output device (5) through a first gear ring (3d) and a gear speed change device (2) in sequence, the power is output outwards through the power output device (5), the rest of the power is transmitted to a first sun gear (3b), a variable pump (4a) and a hydraulic quantitative motor (4b) in sequence by the first planet wheel (3c), then transmitted back to the input shaft (1b) and coupled with the power output to the input shaft (1b) by an engine (1a), wherein the power transmitted to the power output device (5) by the first planet wheel (3c) is greater than the power transmitted to the variable pump (4a) by the first planet wheel (3 c);
when the displacement ratio epsilon of the hydraulic backflow device (4) is less than 0, the first planetary row is locked, and the second planetary row is opened; the output power of the input shaft (1b) is transmitted to the second planet gear (3g) through the first planet carrier (3a), the first planet gear (3c) and the second gear ring (3h) in turn, the second planet gear (3g) transmits partial power to the power output device (5) through the second planet carrier (3e) and the gear speed change device (2) in turn, and the partial power is output outwards by the power output device (5), the second planet wheel (3g) transmits the rest power to a second sun wheel (3f), a variable pump (4a) and a hydraulic quantitative motor (4b) in turn and then transmits the power back to the input shaft (1b), is coupled with the power output by the engine (1a) to the input shaft (1b), the power transmitted by the second planet wheel (3g) to the power output device (5) is larger than the power transmitted by the second planet wheel (3g) to the variable pump (4 a).
2. The dual stage planetary gear return flow hydromechanical continuously variable transmission system of claim 1, wherein: the one end input shaft (1b) of first planet carrier (3a) is connected, and the other end is connected with first planet wheel (3c), the one end and first planet wheel (3c) of second ring gear (3h) are connected, and the other end meshes with second planet wheel (3g), the one end and the second planet wheel (3g) of second planet carrier (3e) are connected, and the other end is connected with gear speed change gear (2), input shaft (1b) is connected with hydraulic pressure ration motor (4b) after passing variable pump (4a), hydraulic pressure ration motor (4b) are connected with variable pump (4a), first sun gear (3b) and second sun gear (3f) all are connected with variable pump (4 a).
3. The dual 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 first sun gear (3b) and the second sun gear (3f) are 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 dual stage planetary gear return flow hydromechanical continuously variable transmission system of claim 1, wherein: gear speed change gear (2) include with first ring gear (3d) synchronous rotation's first variable speed driving gear (2a), with first variable speed driven gear (2b) of first variable speed driving gear (2a) meshing, with second planet carrier (3e) synchronous rotation's second variable speed driving gear (2d) and with second variable speed driven gear (2e) meshing, first variable speed driven gear (2b) can transmit power for power take-off (5) through first clutch (2c), second variable speed driven gear (2e) can transmit power for power take-off (5) through second clutch (2 f).
5. The dual stage planetary gear return flow hydromechanical continuously variable transmission system of claim 4, wherein: the first speed change driving gear (2a) and the first gear ring (3d) are integrally formed, and the second speed change driving gear (2d) and the second planet carrier (3e) are integrally formed.
6. The dual stage planetary gear return flow hydromechanical continuously variable transmission system of claim 4, wherein: the power take-off (5) comprises an output shaft (5a), the output shaft (5a) being drivable by the first clutch (2c) or the second clutch (2 f).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011281448.7A CN112377593A (en) | 2020-11-16 | 2020-11-16 | Double-stage planetary gear return flow type hydraulic mechanical stepless transmission system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011281448.7A CN112377593A (en) | 2020-11-16 | 2020-11-16 | Double-stage planetary gear return flow type hydraulic mechanical stepless transmission system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN112377593A true CN112377593A (en) | 2021-02-19 |
Family
ID=74585533
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011281448.7A Pending CN112377593A (en) | 2020-11-16 | 2020-11-16 | Double-stage planetary gear return flow type hydraulic mechanical stepless transmission system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112377593A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113108036A (en) * | 2021-03-11 | 2021-07-13 | 重庆大学 | Modular heavy load big velocity ratio transmission system modular mechanism |
| CN114087334A (en) * | 2021-11-17 | 2022-02-25 | 浙江盘毂动力科技有限公司 | Hydraulic and mechanical combined type comprehensive transmission device and vehicle |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104329434A (en) * | 2014-08-28 | 2015-02-04 | 江苏大学 | Hydraulic mechanical dual-power flow transmission gearbox |
| CN205298454U (en) * | 2015-11-11 | 2016-06-08 | 潍柴动力股份有限公司 | Hydraulic pressure machinery infinitely variable transmission for loader |
| CN207333618U (en) * | 2017-10-23 | 2018-05-08 | 石河子大学 | A kind of hydraulic mechanical stepless gearbox |
| CN109488740A (en) * | 2019-01-02 | 2019-03-19 | 石河子大学 | A kind of single bipolar system hydraulic mechanical stepless gearbox |
-
2020
- 2020-11-16 CN CN202011281448.7A patent/CN112377593A/en active Pending
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104329434A (en) * | 2014-08-28 | 2015-02-04 | 江苏大学 | Hydraulic mechanical dual-power flow transmission gearbox |
| CN205298454U (en) * | 2015-11-11 | 2016-06-08 | 潍柴动力股份有限公司 | Hydraulic pressure machinery infinitely variable transmission for loader |
| CN207333618U (en) * | 2017-10-23 | 2018-05-08 | 石河子大学 | A kind of hydraulic mechanical stepless gearbox |
| CN109488740A (en) * | 2019-01-02 | 2019-03-19 | 石河子大学 | A kind of single bipolar system hydraulic mechanical stepless gearbox |
Non-Patent Citations (2)
| Title |
|---|
| YU XIA, DONGYE SUN: "Characteristic analysis on a new hydro-mechanical continuously variable transmission system", 《MECHANISM AND MACHINE THEORY》, vol. 126, 10 May 2018 (2018-05-10), pages 457 - 467 * |
| YU XIA, DONGYE SUN等: "Optimisation of the power-cycle hydro-mechanical parameters in a continuously variable transmission designed for agricultural tractors", 《BIOSYSTEMS ENGINEERING》, vol. 193, 27 February 2020 (2020-02-27), pages 12 - 24, XP086131826, DOI: 10.1016/j.biosystemseng.2019.11.009 * |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113108036A (en) * | 2021-03-11 | 2021-07-13 | 重庆大学 | Modular heavy load big velocity ratio transmission system modular mechanism |
| CN114087334A (en) * | 2021-11-17 | 2022-02-25 | 浙江盘毂动力科技有限公司 | Hydraulic and mechanical combined type comprehensive transmission device and vehicle |
| CN114087334B (en) * | 2021-11-17 | 2023-11-03 | 浙江盘毂动力科技有限公司 | Hydraulic mechanical combined type comprehensive transmission device and vehicle |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US6958028B2 (en) | Ranged dual clutch transmission for motor vehicles | |
| US9261181B2 (en) | Continuously variable power-split vehicle transmission | |
| US7083540B2 (en) | Dual clutch transmission having low gear mesh loss | |
| CN2818924Y (en) | Stepless speed variator of multi-sectional continuous hydraulic machinery | |
| CN111946792B (en) | Power split and power confluence combined mechanical-hydraulic compound transmission device | |
| CN109185417B (en) | Quick reversing power-dividing hydraulic mechanical stepless speed changer | |
| CN102943859A (en) | Hydraulic mechanical continuously variable transmission for loader | |
| CN112377593A (en) | Double-stage planetary gear return flow type hydraulic mechanical stepless transmission system | |
| CN108533701B (en) | Multi-section multi-clutch type hydraulic mechanical continuously variable transmission with double planet rows | |
| CN218777413U (en) | Electric drive bridge structure driven by single motor | |
| CN107344492B (en) | Hybrid power system and control method thereof | |
| US7892130B1 (en) | Transmission concept for dual yoke hydrostatic units | |
| CN107246467B (en) | Stepless transmission device for hydraulic machinery of loader | |
| US20140011624A1 (en) | Transmission with disengageable variator | |
| CN212080078U (en) | Multi-stage automatic stepless speed changing box for tractor | |
| RU2399817C2 (en) | Stepless transmission | |
| CN108468781B (en) | Combined double-flow variable-speed transmission device | |
| CN216555172U (en) | Input shaft sectional type transmission | |
| WO2023130420A1 (en) | Continuously variable transmission device having both equal-difference output and equal-ratio output | |
| CN112377592A (en) | Single-stage planetary gear return flow type hydraulic mechanical stepless transmission system | |
| CN110939702B (en) | Compound planet row confluence mechanism | |
| CN112606674B (en) | Electromechanical hybrid transmission stepless speed change structure and vehicle | |
| CN114909453A (en) | Electromechanical-hydraulic composite transmission device and control method thereof | |
| CN112377602A (en) | Control method of backflow type hydraulic mechanical stepless transmission system | |
| US20160097442A1 (en) | Transmission device with secondarily coupled power split |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |