Dual-drive oil pump control method, and dual-drive oil pump system for hybrid power transmission

Abstract

The present application relates to the technical field of hybrid power vehicles, and in particular to a dual-drive oil pump control method, and a dual-drive oil pump system for a hybrid power transmission. The dual-drive oil pump control method comprises: the maximum value of the heat dissipation flow Q1 of a motor, the lubrication flow Q2 of a differential, and the protection flow Q3 of the differential are added to a first compensation flow Q4 to obtain the required flow Qreq of an oil pump; the product of the driving rotating speed S3 of the oil pump, the displacement V of the oil pump, and the volume efficiency η of the oil pump is added to a second compensation flow Q5 to obtain the actual flow Qact of the oil pump; when the actual flow Qact is greater than or equal to the required flow Qreq, the motor does not start, and mechanical drive starts; and when the actual flow Qact is less than the required flow Qreq, the motor starts to a preset rotating speed. The present application can improve the efficiency of a hybrid power transmission, and can effectively reduce the cost of the hybrid power transmission.

Description

Dual-drive oil pump control method and dual-drive oil pump system for hybrid transmission

[0001] Cross-reference to Related Applications

[0002] The present application claims priority to the Chinese patent application No. 202410450147.4 filed on April 15, 2024, and entitled "Dual-drive oil pump control method and dual-drive oil pump system for hybrid transmission", the content of which is incorporated herein by reference in its entirety. TECHNICAL FIELD

[0003] The present application relates to the technical field of hybrid vehicles, in particular to a dual-drive oil pump control method and a dual-drive oil pump system for a hybrid transmission. BACKGROUND

[0004] Most passenger car hybrid transmissions use electro-hydraulic combined control, and the hydraulic oil pump is the power source. The existing oil pump driving mode is mostly single driving mode, i.e. mechanical driving or electric driving part. To meet the demand of the hydraulic system of the hybrid transmission, two sets of oil pump systems are designed, one set uses a mechanical driving oil pump and the other set uses a direct current motor driving oil pump. The two oil pumps are used complementarily, but the cost of independent operation of the two sets of oil pump systems is relatively high. In addition, there are also oil pumps using dual driving mode, but an electromagnetic clutch is used to control the connection between the driving source and the input shaft of the oil pump. This scheme needs to increase the electromagnetic clutch and control circuit, and also has the problem of relatively high cost.

[0005] SUMMARY

[0006] Therefore, the purpose of the present application includes providing a dual-drive oil pump control method and a dual-drive oil pump system for a hybrid transmission to solve the technical problem of high cost of the hybrid transmission using two sets of oil pump systems or an electromagnetic clutch in the prior art to some extent.

[0007] In order to achieve the above-mentioned purpose, the technical solutions adopted by the embodiments of the present application are as follows:

[0008] The present application provides a dual-drive oil pump control method applied to a dual-drive oil pump system of a hybrid transmission in which a mechanical driving and a motor driving are connected to the same oil pump, comprising:

[0009] obtaining a heat dissipation flow rate Q1 of the motor according to the power of the motor, obtaining a lubrication flow rate Q2 of the differential according to a motor driving speed S1, obtaining a protection flow rate Q3 of the differential according to a wheel speed difference S2, obtaining a first compensation flow rate Q4 and a volumetric efficiency η of the oil pump according to an oil temperature T, and obtaining a second compensation flow rate Q5 according to a working cumulative time t of the oil pump;

[0010] The maximum value among the heat dissipation flow rate Q1 of the motor, the lubrication flow rate Q2 of the differential, and the protection flow rate Q3 of the differential is added to the first compensation flow rate Q4 to obtain the required flow rate Qreq of the oil pump;

[0011] The product of the oil pump driving rotation speed S3, the displacement V of the oil pump, and the volumetric efficiency η of the oil pump is added to the second compensation flow rate Q5 to obtain the actual flow rate Qact of the oil pump;

[0012] When the actual flow rate Qact is greater than or equal to the required flow rate Qreq, the motor is not started, and the mechanical drive is started; when the actual flow rate Qact is less than the required flow rate Qreq, the motor is started to a preset rotation speed.

[0013] In the above technical solution, further, the motor driving rotation speed S1 and the torque M of the motor can be obtained according to the power of the motor;

[0014] In the case of S1≤6000rpm:

[0015] When M≤100N·m, Q1=4L / min; when 100N·m

[0016] In the case of 6000rpm

[0017] When M≤50N·m, Q1=4L / min; when 50N·m

[0018] In the case of S1>8000rpm:

[0019] When M≤50N·m, Q1=8L / min; when 50N·m

[0020] In any of the above technical solutions, further, when S1<1000rpm, Q2=4L / min;

[0021] When 1000rpm≤S1<3000rpm, Q2=6L / min;

[0022] When 3000rpm≤S1<5000rpm, Q2=8L / min;

[0023] When 5000rpm≤S1<8000rpm, Q2=10L / min;

[0024] When 8000rpm≤S1<12000rpm, Q2=11L / min;

[0025] When 12000rpm≤S1<14000rpm, Q2=13L / min;

[0026] When 14000rpm≤S1<16000rpm, Q2=15L / min;

[0027] When 16000rpm≤S1<18000rpm, Q2=17L / min;

[0028] When S1≥18000rpm, Q2=18L / min.

[0029] In any of the above technical solutions, further, when 30rpm<S2≤50rpm, Q3=10L / min;

[0030] When 50rpm<S2≤70rpm, Q3=14L / min;

[0031] When S2>70rpm, Q3=18L / min.

[0032] In any of the above technical solutions, further, when -30°C≤T<10°C, Q4=0L / min;

[0033] When 10℃≤T<30℃, Q4=1L / min;

[0034] When 30℃≤T<80℃, Q4=1.5L / min;

[0035] When 80℃≤T<120℃, Q4=2L / min;

[0036] When T≥120℃, Q4=3L / min.

[0037] In any of the above technical solutions, further, when -30°C≤T<30°C, η=0.9%;

[0038] When 30℃≤T<80℃, η=0.85%;

[0039] When 80℃≤T<120℃, η=0.7%;

[0040] When T≥120℃, η=0.6%.

[0041] In any of the above technical solutions, further, 5000h≤t<15000h, Q5=0.1L / min; 15000h≤t<25000h, Q5=0.15L / min;

[0042] t≥25000h, Q5=0.2L / min.

[0043] In any of the above technical solutions, further, the maximum of the mechanical driving speed S4 and the motor driving speed S1 is the oil pump driving speed S3.

[0044] And / or, the preset speed is greater than the mechanical driving speed S4.

[0045] The application also provides a dual-drive oil pump system for a hybrid transmission, comprising a mechanical drive, a motor drive, an oil pump and a connecting assembly, wherein the mechanical drive and the motor drive are connected with the oil pump;

[0046] The connecting assembly comprises a first input shaft connected with the mechanical drive, a second input shaft connected with the motor drive, an output shaft connected with the oil pump and a clutch assembly.

[0047] The clutch assembly comprises a first one-way clutch arranged between the first input shaft and the output shaft and a second one-way clutch arranged between the second input shaft and the output shaft; the first one-way clutch and the second one-way clutch can only rotate in one direction and are locked in the direction of relative rotation, so that the kinetic energy of the mechanical drive can only be transmitted from the first input shaft to the output shaft but not to the second input shaft, and the kinetic energy of the motor drive can only be transmitted from the second input shaft to the output shaft but not to the first input shaft.

[0048] In the above technical solution, further, the connecting assembly further comprises a gear set, the gear set comprising a first driving wheel, a second driving wheel and a driven wheel, the first driving wheel and the second driving wheel being engaged with the driven wheel respectively, the first one-way clutch being arranged between the first driving wheel and the first input shaft, the second one-way clutch being arranged between the second driving wheel and the second input shaft, and the driven wheel being fixed to the output shaft.

[0049] When the first driving wheel rotates, the second input shaft does not rotate; and when the second driving wheel rotates, the second input shaft does not rotate.

[0050] In any of the above technical solutions, further, the first input shaft is connected with the inner ring of the first one-way clutch in interference fit, and the first driving wheel is connected with the outer ring of the first one-way clutch in interference fit.

[0051] And / or, the second input shaft is connected with the inner ring of the second one-way clutch through interference fit, and the second driving wheel is connected with the outer ring of the second one-way clutch through interference fit.

[0052] In any of the above technical solutions, further, the kinetic energy of the mechanical drive comes from the input shaft of the hybrid transmission;

[0053] And / or, the oil pump is an internal gear pump with a single input end.

[0054] Compared with the prior art, the application has the following beneficial effects:

[0055] The double-drive oil pump control method provided by the application comprises:

[0056] The heat dissipation flow rate Q1 of the motor is obtained according to the power of the motor, the lubrication flow rate Q2 of the differential is obtained according to the motor drive speed S1, the protection flow rate Q3 of the differential is obtained according to the wheel speed difference S2, the first compensation flow rate Q4 and the volumetric efficiency η of the oil pump are obtained according to the oil temperature T, and the second compensation flow rate Q5 is obtained according to the cumulative working time t of the oil pump;

[0057] The maximum value among the heat dissipation flow rate Q1 of the motor, the lubrication flow rate Q2 of the differential and the protection flow rate Q3 of the differential is added to the first compensation flow rate Q4 to obtain the required flow rate Qreq of the oil pump;

[0058] The product of the oil pump drive speed S3, the displacement V of the oil pump and the volumetric efficiency η of the oil pump is added to the second compensation flow rate Q5 to obtain the actual flow rate Qact of the oil pump;

[0059] When the actual flow rate Qact is greater than or equal to the required flow rate Qreq, the motor is not started, and the mechanical drive is started; when the actual flow rate Qact is less than the required flow rate Qreq, the motor is started to a preset speed.

[0060] The double-drive oil pump control method provided by the application is applied to a double-drive oil pump system of a hybrid transmission in which a mechanical drive and a motor drive are connected with the same oil pump. In different working conditions, the required flow rate and the actual flow rate of cooling and lubrication during the working of the hybrid transmission are calculated in real time, the optimal speed of the direct-current motor is obtained in combination with the speed of the mechanical drive, the efficiency of the hybrid transmission is improved, and the driving cost is effectively reduced.

[0061] The double-drive oil pump system for the hybrid transmission provided by the application comprises a mechanical drive, a motor drive, an oil pump and a connecting assembly, wherein the mechanical drive and the motor drive are connected with the oil pump;

[0062] The connecting assembly comprises a first input shaft connected with the mechanical drive, a second input shaft connected with the motor drive, an output shaft connected with the oil pump and a clutch assembly.

[0063] The clutch assembly comprises a first one-way clutch arranged between the first input shaft and the output shaft and a second one-way clutch arranged between the second input shaft and the output shaft; the first one-way clutch and the second one-way clutch can only rotate in one direction and are locked in the direction of relative rotation, so that the kinetic energy of the mechanical drive can only be transmitted to the output shaft by the first input shaft and cannot be transmitted to the second input shaft, and the kinetic energy of the motor drive can only be transmitted to the output shaft by the second input shaft and cannot be transmitted to the first input shaft.

[0064] The double-drive oil pump system for the hybrid transmission provided by the application has simple structure and low cost, and the first one-way clutch and the second one-way clutch are used to realize the connection of the same oil pump by the mechanical drive and the motor drive, without the need for additional control, so that the double-drive oil pump system effectively reduces the cost of the hybrid transmission. BRIEF DESCRIPTION OF DRAWINGS

[0065] In order to more clearly illustrate the technical solutions in the specific embodiments or prior art of the present application, the drawings needed in the description of the specific embodiments or prior art will be briefly introduced. Obviously, the drawings in the following description are some embodiments of the present application, and other drawings can also be obtained by those skilled in the art without creative labor.

[0066] Fig. 1 is a flowchart of the double-drive oil pump control method provided by the embodiment of the present application;

[0067] Fig. 2 is a flowchart of obtaining the required flow of the oil pump in the double-drive oil pump control method provided by the embodiment of the present application;

[0068] Fig. 3 is a structural schematic diagram of the double-drive oil pump system for the hybrid transmission provided by the embodiment of the present application;

[0069] Fig. 4 is a structural schematic diagram of the connection assembly in the double-drive oil pump system for the hybrid transmission provided by the embodiment of the present application.

[0070] Reference signs: 1-mechanical drive; 2-motor drive; 3-oil pump; 4-first input shaft; 5-second input shaft; 6-output shaft; 7-first one-way clutch; 8-second one-way clutch; 91-first driving wheel; 92-second driving wheel; 93-driven wheel. DETAILED DESCRIPTION

[0071] The technical solutions of the present application will be described in detail below with reference to the drawings. Obviously, the described embodiments are some embodiments of the present application, not all embodiments.

[0072] The components of the application embodiments, which are generally described and shown in the drawings herein, can be arranged and designed in a variety of different configurations. Therefore, the following detailed description of the embodiments of the application provided in the drawings is not intended to limit the scope of the application, but merely represents selected embodiments of the application.

[0073] All other embodiments obtained by persons of ordinary skill in the art based on the embodiments in the present application without creative labor fall within the scope of protection of the present application.

[0074] In the description of the present application, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore cannot be understood as limiting the present application. In addition, the terms "first", "second", "third" are only for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0075] In the description of the present application, it should be noted that unless otherwise explicitly specified and limited, the terms "mounting", "connecting", "connecting" should be understood broadly, for example, it can be fixedly connected, or it can be detachably connected, or integrally connected; it can be mechanically connected, or it can be electrically connected; it can be directly connected, or it can be indirectly connected through an intermediate medium; it can be the communication inside two elements. For those of ordinary skill in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances.

[0076] The dual-drive oil pump control method and the dual-drive oil pump system for a hybrid transmission according to the embodiments of the present application will be described below with reference to FIGS. 1 and 2.

[0077] The dual-drive oil pump control method comprises:

[0078] Step S10, obtaining an actual flow Qact; wherein the actual flow Qact is an actual output flow of the oil pump for cooling and lubricating the oil of the hybrid transmission under different working conditions.

[0079] Step S20, obtaining a required flow Qreq; wherein the required flow Qreq is an oil flow required to meet the cooling and lubrication requirements of the hybrid transmission during operation according to the heat generation inside the transmission; it should be noted that the calculation sequence of steps S10 and S20 is not sequential.

[0080] Step S30, compare the actual flow Qact and the required flow Qreq, if the actual flow Qact≥ the required flow Qreq, execute the following step S41; if the actual flow Qact< the required flow Qreq, execute the following step S42.

[0081] Step S41, the motor is not started, the mechanical drive is started, that is, only the mechanical drive provides kinetic energy for the oil pump.

[0082] Step S42, the motor is started to a preset rotating speed, realizing that only the motor provides kinetic energy for the oil pump.

[0083] The preset rotating speed is greater than the mechanical drive rotating speed S4, and in the case of the actual flow Qact< the required flow Qreq, the rotating speed of the input end of the oil pump is synchronized with the rotating speed of the motor, that is, the preset rotating speed, so that the optimal rotating speed of the direct current motor can be obtained, the efficiency of the hybrid transmission is improved, and the driving cost is effectively reduced.

[0084] The required flow Qreq of the oil pump considers four factors, factor 1 is the flow requirement of motor cooling, that is, corresponding to the following Q1; factor 2 is the cooling and lubrication flow requirement between the shaft teeth of the differential, that is, corresponding to the following Q2; factor 3 is that the too large rotating speed difference of the differential is easy to cause damage to the differential, that is, corresponding to the following Q3; factor 4 is the influence of oil temperature on the cooling and lubrication effect, that is, corresponding to the following Q4; specifically, as shown in FIG. 2, the steps of obtaining the required flow Qreq of the oil pump are as follows:

[0085] Step S21, obtaining the heat dissipation flow Q1 of the motor according to the power of the motor.

[0086] Preferably, the motor drive rotating speed S1 and the torque M of the motor can be obtained according to the power of the motor, wherein the motor drive rotating speed S1 and the torque M of the motor can be obtained by looking up a table.

[0087] Wherein, the relationship between the motor drive rotating speed S1 and the torque M of the motor and the value of the heat dissipation flow Q1 of the motor is as follows:

[0088] In the case of S1≤6000rpm:

[0089] When M≤100N·m, Q1=4L / min; when 100N·m

[0090] In the case of 6000rpm

[0091] When M≤50 N·m, Q1=4 L / min; when 50 N·m

[0092] When S1>8000 rpm:

[0093] When M≤50 N·m, Q1=8 L / min; when 50 N·m

[0094] For example, when S1=7000 rpm and M=135.8 Nxm, the value of Q1 is 12 L / min.

[0095] Step S22, obtaining the lubrication flow Q2 of the differential according to the motor driving speed S1.

[0096] Preferably, the relationship between the motor driving speed S1 and the value of the lubrication flow Q2 of the differential is as follows:

[0097] When S1<1000 rpm, Q2=4 L / min; when 1000 rpm≤S1<3000 rpm, Q2=6 L / min; when 3000 rpm≤S1<5000 rpm, Q2=8 L / min; when 5000 rpm≤S1<8000 rpm, Q2=10 L / min; when 8000 rpm≤S1<12000 rpm, Q2=11 L / min; when 12000 rpm≤S1<14000 rpm, Q2=13 L / min; when 14000 rpm≤S1<16000 rpm, Q2=15 L / min; when 16000 rpm≤S1<18000 rpm, Q2=17 L / min; and when S1≥18000 rpm, Q2=18 L / min.

[0098] For example, when S1=7000 rpm, the value of Q2 is 10 L / min.

[0099] Step S23, obtaining the protection flow Q3 of the differential according to the wheel speed difference S2, wherein the wheel speed difference S2 is the difference between the rotational speeds of the outer wheel and the inner wheel connected to the differential.

[0100] Preferably, the relationship between the wheel speed difference S2 and the value of the protection flow Q3 of the differential is as follows:

[0101] Q3 = 10 L / min when 30 rpm < S2≤ 50 rpm; Q3 = 14 L / min when 50 rpm < S2≤ 70 rpm; Q3 = 18 L / min when S2> 70 rpm.

[0102] For example, when S2= 48 rpm, Q3= 10 L / min.

[0103] Step S24, obtaining a first compensation flow Q4 according to the oil temperature T.

[0104] Preferably, the relationship between the oil temperature T and the value of the first compensation flow Q4 is as follows:

[0105] Q4 = 0 L / min when -30℃≤ T < 10℃; Q4 = 1 L / min when 10℃≤ T < 30℃; Q4 = 1.5 L / min when 30℃≤ T < 80℃; Q4 = 2 L / min when 80℃≤ T < 120℃; Q4 = 3 L / min when T≥ 120℃.

[0106] For example, when T = 80℃, Q4= 2 L / min.

[0107] It should be noted that the calculation order of Q1, Q2, Q3 and Q4 is not sequential, that is, the execution order of steps S21, S22, S23 and S24 is not sequential.

[0108] Step S25, the maximum value of the heat dissipation flow Q1 of the motor, the lubrication flow Q2 of the differential and the protection flow Q3 of the differential is added to the first compensation flow Q4 to obtain the required flow Qreq of the oil pump; that is, Qreq = max(Q1, Q2, Q3) + Q4.

[0109] For example, when Q1 = 12 L / min, Q2 = 10 L / min, Q3 = 10 L / min, Q4 = 2 L / min, Qreq = 14 L / min.

[0110] More specifically, the steps of obtaining the actual flow Qact of the oil pump are as follows:

[0111] Step S11, obtaining the oil pump drive speed S3, the displacement V of the oil pump and the volumetric efficiency η of the oil pump.

[0112] In step S11, the maximum value of the mechanical drive speed S4 and the motor drive speed S1 is the oil pump drive speed S3. The displacement V of the oil pump can be calculated according to the model parameters of the selected oil pump.

[0113] Further, in step S11, a step S111 of obtaining the volumetric efficiency η of the oil pump according to the oil temperature T is further included, wherein the oil temperature T can be obtained by measuring through a temperature sensor.

[0114] Preferably, the relationship between the oil temperature T and the value of the volumetric efficiency η of the oil pump is as follows:

[0115] When -30℃≤T<30℃, η=0.9%; when 30℃≤T<80℃, η=0.85%; when 80℃≤T<120℃, η=0.7%; and when T≥120℃, η=0.6%.

[0116] For example, in the case of T=80℃, the value of η is 0.7%.

[0117] Step S12, obtaining the second compensation flow Q5 according to the cumulative working time t of the oil pump; wherein the cumulative working time t of the oil pump can be obtained from the control panel of the oil pump; it should be noted that the calculation order of step S11 and step S12 is not sequential.

[0118] Preferably, the relationship between the cumulative working time t of the oil pump and the value of the second compensation flow Q5 is as follows:

[0119] When 5000h≤t<15000h, Q5=0.1L / min; when 15000h≤t<25000h, Q5=0.15L / min; and when t≥25000h, Q5=0.2L / min.

[0120] For example, in the case of t=40000h, the value of Q5 is 0.2L / min.

[0121] Step S13, the product of the oil pump drive speed S3, the displacement V of the oil pump and the volumetric efficiency η of the oil pump is added to the second compensation flow Q5 to obtain the actual flow Qact of the oil pump, i.e. Qact=S3×V×η+Q5.

[0122] It should be noted that the corresponding relationship between the value of different flows and each parameter can be obtained according to software simulation and / or actual experience, or can be obtained by actual measurement.

[0123] According to the double-drive oil pump control method provided by the application, the double-drive oil pump system is applied to a hybrid transmission with a mechanical drive and a motor drive connected to the same oil pump. In different working conditions, the demand flow and the actual flow of the hybrid transmission during cooling and lubrication are calculated in real time, the optimal speed of the direct-current motor is obtained in combination with the speed of the mechanical drive, the efficiency of the hybrid transmission is improved, and the driving cost is effectively reduced.

[0124] A dual drive oil pump system for a hybrid transmission is described below with reference to Figs. 3 and 4, including a mechanical drive 1, an electric drive 2, an oil pump 3 and a connecting assembly according to embodiments of the present application.

[0125] As shown in Figs. 3 and 4, the mechanical drive 1 and the electric drive 2 are both connected to the oil pump 3, wherein the mechanical drive 1 can be powered by the input shaft of the hybrid transmission, and the electric drive 2 can be powered by a direct current motor.

[0126] Preferably, the oil pump 3 is an internal gear pump with a single input end.

[0127] Specifically, in the present embodiment, as shown in Figs. 3 and 4, the connecting assembly includes a first input shaft 4 connected to the mechanical drive 1, a second input shaft 5 connected to the electric drive 2, an output shaft 6 connected to the oil pump 3, and a clutch assembly, wherein the first input shaft 4, the second input shaft 5 and the output shaft 6 can be arranged in parallel to each other, and the output shaft 6 is connected to the input end of the oil pump 3.

[0128] Further, in the present embodiment, as shown in Figs. 3 and 4, the clutch assembly includes a first one-way clutch 7 arranged between the first input shaft 4 and the output shaft 6, and a second one-way clutch 8 arranged between the second input shaft 5 and the output shaft 6, wherein the first one-way clutch 7 and the second one-way clutch 8 can only rotate in one direction and are locked in the direction of relative rotation, so that the mechanical drive 1 can only power the output shaft 6 through the first input shaft 4, but not the second input shaft 5, and the electric drive 2 can only power the output shaft 6 through the second input shaft 5, but not the first input shaft 4.

[0129] Specifically, the first one-way clutch 7 and the second one-way clutch 8 can both be a one-way clutch, which includes an inner ring, an outer ring, a retainer and a wedge block, wherein when the inner ring is fixed, the outer ring can rotate in the clockwise direction, at which time the wedge block does not lock, allowing the inner ring to rotate freely, and when the outer ring rotates in the counterclockwise direction, the wedge block locks to prevent the outer ring from continuing to rotate. The one-way clutch is widely used, low in price, and does not require additional control, thereby reducing the cost of the hybrid transmission.

[0130] The first one-way clutch 7 and the second one-way clutch 8 rotate in the same direction.

[0131] Further, in the embodiment, as shown in FIG. 3 and FIG. 4, the connecting assembly further comprises a gear set, the gear set comprises a first driving wheel 91, a second driving wheel 92 and a driven wheel 93, the first driving wheel 91 and the second driving wheel 92 are respectively engaged with the driven wheel 93, the first driving wheel 91 and the second driving wheel 92 are not engaged to realize power transmission. The first driving wheel 91 and the second driving wheel 92 can be arranged at two ends of the driven wheel 93 in the radial direction, the first one-way clutch 7 is arranged between the first driving wheel 91 and the first input shaft 4, the second one-way clutch 8 is arranged between the second driving wheel 92 and the second input shaft 5, and the driven wheel 93 is fixed to the output shaft 6, so as to realize that when the first driving wheel 91 rotates, the second input shaft 5 does not rotate; and when the second driving wheel 92 rotates, the first input shaft 4 does not rotate.

[0132] Further, in the embodiment, as shown in FIG. 3 and FIG. 4, the first input shaft 4 is connected with the inner ring of the first one-way clutch 7 in an interference fit, and the first driving wheel 91 is connected with the outer ring of the first one-way clutch 7 in an interference fit. Preferably, the second input shaft 5 is connected with the inner ring of the second one-way clutch 8 in an interference fit, and the second driving wheel 92 is connected with the outer ring of the second one-way clutch 8 in an interference fit.

[0133] Specifically, when the mechanical drive 1 works, it drives the first input shaft 4 to rotate clockwise, and then drives the first one-way clutch and the first driving wheel 91 to rotate clockwise by the first input shaft 4, so that the driven wheel 93 engaged with the first driving wheel 91 drives the output shaft 6 to rotate counterclockwise, at this time, the driven wheel 93 also drives the second driving wheel 92 to rotate clockwise, but under the action of the second one-way clutch 8, the second driving wheel 92 cannot drive the second input shaft 5 to rotate clockwise, so the second input shaft 5 has no rotating tendency.

[0134] More specifically, when the motor drive 2 works, it drives the second input shaft 5 to rotate clockwise, and then drives the second one-way clutch and the second driving wheel 92 to rotate clockwise by the second input shaft 5, so that the driven wheel 93 engaged with the second driving wheel 92 drives the output shaft 6 to rotate counterclockwise, at this time, the driven wheel 93 also drives the first driving wheel 91 to rotate clockwise, but under the action of the first one-way clutch 7, the first driving wheel 91 cannot drive the first input shaft 4 to rotate clockwise, so the first input shaft 4 has no rotating tendency.

[0135] According to the double-drive oil pump system for the hybrid transmission provided by the present application, the structure is simple and the cost is low, the first one-way clutch and the second one-way clutch are used to realize the connection of the mechanical drive and the motor drive to the same oil pump, without additional control, so that the double-drive oil pump system effectively reduces the cost of the hybrid transmission.

[0136] It should be finally pointed out that the above embodiments are only used to illustrate the technical solutions of the present application, but not to limit them; although the present application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that the technical solutions recorded in the foregoing embodiments can still be modified, or some or all of the technical features can be replaced equivalently; and these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the scope of the technical solutions of the embodiments of the present application. Industrial applicability

[0137] The double-drive oil pump control method provided by the present application calculates the required flow and the actual flow of the cooling and lubrication of the hybrid transmission in real time under different working conditions, combines the speed of the mechanical drive to obtain the optimal speed of the DC motor, improves the efficiency of the hybrid transmission, and effectively reduces the driving cost. The double-drive oil pump system for the hybrid transmission uses the first one-way clutch and the second one-way clutch to realize the connection of the mechanical drive and the motor drive to the same oil pump, without additional control, so that the double-drive oil pump system effectively reduces the cost of the hybrid transmission.

Claims

1. A dual drive oil pump control method applied to a dual drive oil pump system of a hybrid transmission in which a mechanical drive and a motor drive are connected to the same oil pump, characterized by, Comprise: According to the power of the motor, the heat dissipation flow rate Q1 of the motor is obtained, according to the motor driving speed S1, the lubrication flow rate Q2 of the differential is obtained, according to the wheel speed difference S2, the protection flow rate Q3 of the differential is obtained, according to the oil temperature T, the first compensation flow rate Q4 and the volumetric efficiency η of the oil pump are obtained, and according to the working cumulative length t of the oil pump, the second compensation flow rate Q5 is obtained; The maximum value of the heat dissipation flow rate Q1 of the motor, the lubrication flow rate Q2 of the differential and the protection flow rate Q3 of the differential is added to the first compensation flow rate Q4 to obtain the required flow rate Qreq of the oil pump; The product of the oil pump driving speed S3, the displacement V of the oil pump and the volumetric efficiency η of the oil pump is added to the second compensation flow rate Q5 to obtain the actual flow rate Qact of the oil pump; When the actual flow rate Qact is greater than or equal to the required flow rate Qreq, the motor is not started, and the mechanical drive is started; when the actual flow rate Qact is less than the required flow rate Qreq, the motor is started to a preset speed.

2. The dual drive fuel pump control method of claim 1, wherein, According to the power of the motor, the motor driving speed S1 and the torque M of the motor can be obtained; In the case of S1≤6000rpm: When M≤100N·m, Q1=4L / min; when 100N·m<M≤150N·m, Q1=8L / min; when 150N·m<M≤200N·m, Q1=12L / min; when 200N·m<M≤300N·m, Q1=16L / min; when M>300N·m, Q1=18L / min; In the case of 6000rpm<S1≤8000rpm: When M≤50N·m, Q1=4L / min; when 50N·m<M≤100N·m, Q1=8L / min; when 100N·m<M≤150N·m, Q1=12L / min; when 150N·m<M≤250N·m, Q1=16L / min; when M>250N·m, Q1=18L / min; In the case of S1>8000rpm: When M≤50N·m, Q1=8L / min; when 50N·m<M≤100N·m, Q1=12L / min; when 100N·m<M≤200N·m, Q1=16L / min; when M>200Nxm, Q1=18L / min.

3. The dual-drive oil pump control method according to claim 1, wherein: When S1<1000rpm, Q2=4L / min; When 1000rpm≤S1<3000rpm, Q2=6L / min; When 3000rpm≤S1<5000rpm, Q2=8L / min; When 5000rpm≤S1<8000rpm, Q2=10L / min; When 8000rpm≤S1<12000rpm, Q2=11L / min; When 12000rpm≤S1<14000rpm, Q2=13L / min; When 14000rpm≤S1<16000rpm, Q2=15L / min; When 16000rpm≤S1<18000rpm, Q2=17L / min; S1≥18000rpm, Q2=18L / min.

4. The dual-drive oil pump control method according to claim 1, wherein, 30rpm 50rpm S2>70rpm, Q3=18L / min.

5. The dual-drive oil pump control method according to claim 1, wherein, -30℃≤T<10℃, Q4=0L / min; 10℃≤T<30℃, Q4=1L / min; 30℃≤T<80℃, Q4=1.5L / min; 80℃≤T<120℃, Q4=2L / min; T≥120℃, Q4=3L / min.

6. The dual-drive oil pump control method according to claim 1, wherein, -30℃≤T<30℃, η=0.9%; 30℃≤T<80℃, η=0.85%; 80℃≤T<120℃, η=0.7%; T≥120℃, η=0.6%.

7. The dual-drive oil pump control method according to claim 1, wherein, 5000h≤t<15000h, Q5=0.1L / min; 15000h≤t<25000h, Q5=0.15L / min; t≥25000h, Q5=0.2L / min.

8. The dual drive fuel pump control method of claim 1, wherein, The maximum value between the mechanical drive rotating speed S4 and the motor drive rotating speed S1 is the oil pump drive rotating speed S3. And / or, the preset rotating speed is greater than the mechanical drive rotating speed S4.

9. A dual drive oil pump system for a hybrid transmission, characterized by, Comprise: a mechanical drive, a motor drive, an oil pump and a connecting assembly, the mechanical drive and the motor drive are connected with the oil pump; the connecting assembly comprises a first input shaft connected with the mechanical drive, a second input shaft connected with the motor drive and an output shaft connected with the oil pump and a clutch assembly; the clutch assembly comprises a first one-way clutch arranged between the first input shaft and the output shaft and a second one-way clutch arranged between the second input shaft and the output shaft; the first one-way clutch and the second one-way clutch can only rotate in one direction and are locked in the direction of relative rotation, so that the kinetic energy of the mechanical drive can only be transmitted from the first input shaft to the output shaft, but not to the second input shaft, and the kinetic energy of the motor drive can only be transmitted from the second input shaft to the output shaft, but not to the first input shaft.

10. The dual drive oil pump system for a hybrid transmission of claim 9, wherein, the connecting assembly further comprises a gear set, the gear set comprises a first driving wheel, a second driving wheel and a driven wheel, the first driving wheel and the second driving wheel are engaged with the driven wheel respectively, the first one-way clutch is arranged between the first driving wheel and the first input shaft, the second one-way clutch is arranged between the second driving wheel and the second input shaft, and the driven wheel is fixed to the output shaft; when the first driving wheel rotates, the second input shaft does not rotate; when the second driving wheel rotates, the second input shaft does not rotate.

11. The dual drive oil pump system for a hybrid transmission of claim 10, wherein, The first input shaft is connected with the inner ring of the first one-way clutch in interference fit, and the first driving wheel is connected with the outer ring of the first one-way clutch in interference fit; And / or, the second input shaft is connected with the inner ring of the second one-way clutch in interference fit, and the second driving wheel is connected with the outer ring of the second one-way clutch in interference fit.

12. The dual drive oil pump system for a hybrid transmission of claim 9, wherein, The mechanical driving kinetic energy comes from the input shaft of the hybrid transmission; And / or, the oil pump is an internal gear pump with a single input end.

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