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

Abstract

The present invention relates to the technical field of hybrid vehicles, and particularly to a dual-drive oil pump control method and a dual-drive oil pump system for a hybrid transmission. The dual-drive oil pump control method includes: adding 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 to the first compensation flow rate Q4 to obtain the required flow rate Qreq of the oil pump; adding 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 to the second compensation flow rate Q5 to obtain the actual flow rate Qact of the oil pump; when the actual flow rate Qact ≥ the required flow rate Qreq, the motor does not start and the mechanical drive starts; when the actual flow rate Qact < the required flow rate Qreq, the motor starts to a preset speed. The present invention can improve the efficiency of the hybrid transmission and effectively reduce the cost of the hybrid transmission.

Description

Technical Field

[0001] The present invention relates to the technical field of hybrid vehicles, and in particular to a dual-drive oil pump control method and a dual-drive oil pump system for a hybrid transmission. Background Art

[0002] Most passenger car hybrid transmissions adopt electro-hydraulic combined control, and the hydraulic oil pump is the power source. The existing oil pump drive methods are mostly single drive methods, that is, mechanical drive or electric drive parts. To meet the requirements of the hydraulic system of the hybrid transmission, two sets of oil pump systems are designed, one set uses a mechanically driven oil pump, and the other set uses a DC motor-driven oil pump. The two oil pumps are used complementarily, but the independent operation cost of the two sets of oil pump systems is relatively high; in addition, there are also oil pumps using a dual-drive method, but an electromagnetic clutch is used to control the connection between the drive source and the oil pump input shaft. This solution requires adding an electromagnetic clutch and a control circuit, and there is also a problem of high cost. Summary of the Invention

[0003] In view of this, the purpose of this application is to provide a dual-drive oil pump control method and a dual-drive oil pump system for a hybrid transmission to solve the problem of high cost in existing hybrid transmissions using two sets of oil pump systems or electromagnetic clutches.

[0004] The first aspect of the present invention provides a dual-drive oil pump control method, which is applied to a dual-drive oil pump system of a hybrid transmission in which a mechanical drive and an electric motor drive are connected to the same oil pump. Among them, it includes:

[0005] Obtain the heat dissipation flow rate Q1 of the motor according to the power of the motor, obtain the lubrication flow rate Q2 of the differential according to the motor drive speed S1, obtain the protection flow rate Q3 of the differential according to the wheel speed difference S2, obtain the first compensation flow rate Q4 and the volumetric efficiency η of the oil pump according to the oil temperature T, and obtain the second compensation flow rate Q5 according to the working cumulative duration t of the oil pump;

[0006] The sum of 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 and the first compensation flow rate Q4 is the required flow rate Qreq of the oil pump;

[0007] 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 plus the second compensation flow rate Q5 is the actual flow rate Qact of the oil pump;

[0008] When the actual flow rate Qact ≥ the required flow rate Qreq, the motor does not start and the mechanical drive starts; when the actual flow rate Qact < the required flow rate Qreq, the motor starts to a preset speed.

[0009] Preferably, the motor drive speed S1 and the torque M of the motor can be obtained according to the power of the motor;

[0010] When S1 ≤ 6000 rpm:

[0011] When M ≤ 100 N·m, Q1 = 4 L / min; when 100 N·m < M ≤ 150 N·m, Q1 = 8 L / min;

[0012] when 150 N·m < M ≤ 200 N·m, Q1 = 12 L / min; when 200 N·m < M ≤ 300 N·m, Q1 = 16 L / min; when M > 300 N·m, Q1 = 18 L / min;

[0013] When 6000 rpm < S1 ≤ 8000 rpm:

[0014] When M ≤ 50 N·m, Q1 = 4 L / min; when 50 N·m < M ≤ 100 N·m, Q1 = 8 L / min;

[0015] when 100 N·m < M ≤ 150 N·m, Q1 = 12 L / min; when 150 N·m < M ≤ 250 N·m, Q1 = 16 L / min; when M > 250 N·m, Q1 = 18 L / min;

[0016] When S1 > 8000 rpm:

[0017] When M ≤ 50 N·m, Q1 = 8 L / min; when 50 N·m < M ≤ 100 N·m, Q1 = 12 L / min;

[0018] when 100 N·m < M ≤ 200 N·m, Q1 = 16 L / min; when M > 200 N·m, Q1 = 18 L / min.

[0019] Preferably, when S1 < 1000 rpm, Q2 = 4 L / min;

[0020] when 1000 rpm ≤ S1 < 3000 rpm, Q2 = 6 L / min;

[0021] when 3000 rpm ≤ S1 < 5000 rpm, Q2 = 8 L / min;

[0022] when 5000 rpm ≤ S1 < 8000 rpm, Q2 = 10 L / min;

[0023] when 8000 rpm ≤ S1 < 12000 rpm, Q2 = 11 L / min;

[0024] when 12000 rpm ≤ S1 < 14000 rpm, Q2 = 13 L / min;

[0025] When 14000 rpm ≤ S1 < 16000 rpm, Q2 = 15 L / min;

[0026] When 16000 rpm ≤ S1 < 18000 rpm, Q2 = 17 L / min;

[0027] When S1 ≥ 18000 rpm, Q2 = 18 L / min.

[0028] Preferably, when 30 rpm < S2 ≤ 50 rpm, Q3 = 10 L / min;

[0029] When 50 rpm < S2 ≤ 70 rpm, Q3 = 14 L / min;

[0030] When S2 > 70 rpm, Q3 = 18 L / min.

[0031] Preferably, when -30°C ≤ T < 10°C, Q4 = 0 L / min;

[0032] When 10°C ≤ T < 30°C, Q4 = 1 L / min;

[0033] When 30°C ≤ T < 80°C, Q4 = 1.5 L / min;

[0034] When 80°C ≤ T < 120°C, Q4 = 2 L / min;

[0035] When T ≥ 120°C, Q4 = 3 L / min.

[0036] Preferably, when -30°C ≤ T < 30°C, η = 0.9%;

[0037] When 30°C ≤ T < 80°C, η = 0.85%;

[0038] When 80°C ≤ T < 120°C, η = 0.7%;

[0039] When T ≥ 120°C, η = 0.6%.

[0040] Preferably, when 5000 h ≤ t < 15000 h, Q5 = 0.1 L / min;

[0041] When 15000 h ≤ t < 25000 h, Q5 = 0.15 L / min;

[0042] When t ≥ 25000 h, Q5 = 0.2 L / min.

[0043] Preferably, the maximum value of the mechanical drive speed S4 and the motor drive speed S1 is the oil pump drive speed S3;

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

[0045] The second aspect of the present invention provides a dual-drive oil pump system for a hybrid transmission, which includes: a mechanical drive, an electric drive, an oil pump, and a connection assembly, wherein the mechanical drive and the electric drive are both connected to the oil pump;

[0046] The connection assembly includes a first input shaft connected to the mechanical drive, a second input shaft connected to the electric drive, an output shaft connected to the oil pump, and a clutch assembly;

[0047] The clutch assembly includes a first one-way clutch member disposed between the first input shaft and the output shaft and a second one-way clutch member disposed between the second input shaft and the output shaft; the first one-way clutch member and the second one-way clutch member 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 and cannot be transmitted to the second input shaft, and the kinetic energy of the electric drive can only be transmitted from the second input shaft to the output shaft and cannot be transmitted to the first input shaft.

[0048] Preferably, the connection assembly further includes a gear set, which includes a first driving wheel, a second driving wheel, and a driven wheel. The first driving wheel and the second driving wheel are respectively meshed with the driven wheel. The first one-way clutch member is disposed between the first driving wheel and the first input shaft, the second one-way clutch member is disposed between the second driving wheel and the second input shaft, and the driven wheel is fixed to the output shaft;

[0049] 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.

[0050] Preferably, the first input shaft is connected to the inner ring of the first one-way clutch member by interference fit, and the first driving wheel is connected to the outer ring of the first one-way clutch member by interference fit;

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

[0052] Preferably, 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 beneficial effects of the present invention are:

[0055] The dual-drive oil pump control method of the present invention is applied to a dual-drive oil pump system of a hybrid transmission in which mechanical drive and motor drive are connected to the same oil pump. Under different working conditions, the required flow rate and actual flow rate for cooling and lubrication during the operation of the hybrid transmission are calculated in real time, and the optimal speed of the DC motor is obtained in combination with the speed of the mechanical drive, thereby improving the efficiency of the hybrid transmission and effectively reducing the drive cost.

[0056] The dual-drive oil pump system for a hybrid transmission according to the present invention has a simple structure and low cost. By using the first one-way clutch and the second one-way clutch to connect the mechanical drive and the motor drive to the same oil pump without additional control, the cost of the hybrid transmission is effectively reduced by the dual-drive oil pump system.

[0057] To make the above objects, features, and advantages of the present application more obvious and understandable, the following specifically enumerates preferred embodiments and, in conjunction with the accompanying drawings, details are described as follows. Description of the Drawings

[0058] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following will briefly introduce the drawings required for use in the description of the specific embodiments or the prior art. Obviously, the drawings in the following description are some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can also be obtained based on these drawings.

[0059] Figure 1 A flowchart of the dual-drive oil pump control method provided by the embodiment of the present invention;

[0060] Figure 2 A flowchart of obtaining the required flow rate of the oil pump in the dual-drive oil pump control method provided by the embodiment of the present invention;

[0061] Figure 3 A structural diagram of the dual-drive oil pump system for a hybrid transmission provided by the embodiment of the present invention;

[0062] Figure 4 A structural diagram of the connection component in the dual-drive oil pump system for a hybrid transmission provided by the embodiment of the present invention.

[0063] Icons: 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 Embodiments

[0064] The following specific embodiments are provided to assist the reader in obtaining a comprehensive understanding of the methods, apparatuses, and / or systems described herein. However, after understanding the disclosure of this application, various changes, modifications, and equivalents of the methods, apparatuses, and / or systems described herein will be apparent. For example, the order of operations described herein is merely exemplary and is not limited to the order set forth herein, but rather changes that will be apparent after understanding the disclosure of this application may be made, except for operations that must occur in a specific order. Additionally, descriptions of features known in the art may be omitted for increased clarity and conciseness.

[0065] The features described herein may be implemented in different forms and should not be construed as limited to the examples described herein. Rather, the examples described herein are provided only to illustrate some of the many possible ways of implementing the methods, apparatuses, and / or systems described herein that will be apparent after understanding the disclosure of this application.

[0066] Throughout the specification, when an element (such as a layer, region, or substrate) is described as "on" another element, "connected to" another element, "bonded to" another element, "above" another element, or "covering" another element, it may be directly "on", "connected to", "bonded to", "above", or "covering" the other element, or there may be one or more other elements therebetween. In contrast, when an element is described as "directly on", "directly connected to", "directly bonded to", "directly above", or "directly covering" another element, there may be no other elements therebetween.

[0067] As used herein, the term "and / or" includes any one of the listed related items and any combination of any two or more of them.

[0068] Although terms such as "first", "second", and "third" may be used herein to describe various members, components, regions, layers, or parts, these members, components, regions, layers, or parts are not limited by these terms. Rather, these terms are only used to distinguish one member, component, region, layer, or part from another. Thus, the first member, component, region, layer, or part referred to in the examples described herein may also be referred to as the second member, component, region, layer, or part without departing from the teachings of the examples.

[0069] For ease of description, spatial relationship terms such as "above", "upper", "below", and "lower" may be used herein to describe the relationship of one element to another as shown in the drawings. Such spatial relationship terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the drawings. For example, if the device in the drawings is flipped, an element described as "above" or "upper" relative to another element will then be "below" or "lower" relative to the other element. Thus, the term "above" includes both the orientation of "above" and "below" depending on the spatial orientation of the device. The device may also be positioned in other ways (e.g., rotated 90 degrees or in other orientations), and the spatial relationship terms used herein will be interpreted accordingly.

[0070] The terms used herein are for the purpose of describing various examples only and are not intended to limit the disclosure. Unless the context clearly dictates otherwise, the singular forms are also intended to include the plural forms. The terms "comprises", "comprising", and "having" list the stated features, quantities, operations, components, elements, and / or combinations thereof that exist, but do not preclude the presence or addition of one or more other features, quantities, operations, components, elements, and / or combinations thereof.

[0071] Due to manufacturing techniques and / or tolerances, variations in the shapes shown in the drawings may occur. Thus, the examples described herein are not limited to the specific shapes shown in the drawings, but include changes in shape that occur during manufacturing.

[0072] The features of the examples described herein may be combined in various ways that will be apparent after understanding the disclosure of the present application. In addition, although the examples described herein have a variety of configurations, other configurations are possible as will be apparent after understanding the disclosure of the present application.

[0073] According to a first aspect of the present invention, a dual-drive oil pump control method is provided, which is applied to a dual-drive oil pump system of a hybrid transmission in which mechanical drive and motor drive are connected to the same oil pump.

[0074] In this embodiment, as Figure 1 shown, the dual-drive oil pump control method includes:

[0075] Step S10: Obtain the actual flow rate Qact; where the actual flow rate Qact is the actual output flow rate of the oil pump for cooling and lubricating the hybrid transmission under different operating conditions.

[0076] Step S20: Obtain the required flow rate Qreq; where the required flow rate Qreq is the oil flow rate that meets the cooling and lubrication requirements during the operation of the hybrid transmission according to the heat generation situation inside the transmission under different working conditions. It should be noted that the calculation order of Step S10 and Step S20 is not sequential.

[0077] Step S30: Compare the magnitudes of the actual flow rate Qact and the required flow rate Qreq. If the actual flow rate Qact ≥ the required flow rate Qreq, execute the following Step S41; if the actual flow rate Qact < the required flow rate Qreq, execute the following Step S42.

[0078] Step S41: The motor does not start, and the mechanical drive starts, that is, only the mechanical drive provides kinetic energy for the oil pump.

[0079] Step S42: The motor starts to a preset speed to achieve that only the motor provides kinetic energy for the oil pump.

[0080] In this embodiment, the preset speed is greater than the mechanical drive speed S4. When the actual flow rate Qact < the required flow rate Qreq, the speed at the input end of the oil pump is synchronized with the speed of the motor, which is the preset speed. In this way, the optimal speed of the DC motor can be obtained, improving the efficiency of the hybrid transmission and effectively reducing the drive cost.

[0081] In this embodiment, four factors are considered for the required flow rate Qreq of the oil pump. Factor 1 is the flow rate requirement for motor cooling, that is, corresponding to Q1 below; Factor 2 is the cooling and lubrication flow rate requirement between the shaft gears of the differential, that is, corresponding to Q2 below; Factor 3 is that an excessive speed difference of the differential is likely to damage the differential, that is, corresponding to Q3 below; Factor 4 is the influence of the oil temperature on the cooling and lubrication effect, that is, corresponding to Q4 below; Specifically, as Figure 2 shown, the steps to obtain the required flow rate Qreq of the oil pump are as follows:

[0082] Step S21: Obtain the heat dissipation flow rate Q1 of the motor according to the power of the motor.

[0083] Preferably, in this embodiment, the motor drive speed S1 and the torque M of the motor can be obtained according to the power of the motor, and the motor drive speed S1 and the torque M of the motor can be obtained by looking up a table.

[0084] Among them, the relationship between the motor drive speed S1 and the torque M of the motor and the value of the heat dissipation flow rate Q1 of the motor is as follows:

[0085] In the case of S1 ≤ 6000 rpm:

[0086] When M ≤ 100 N·m, Q1 = 4 L / min; when 100 N·m < M ≤ 150 N·m, Q1 = 8 L / min; when 150 N·m < M ≤ 200 N·m, Q1 = 12 L / min; when 200 N·m < M ≤ 300 N·m, Q1 = 16 L / min; when M > 300 N·m, Q1 = 18 L / min.

[0087] In the case of 6000 rpm < S1 ≤ 8000 rpm:

[0088] When M ≤ 50 N·m, Q1 = 4 L / min; when 50 N·m < M ≤ 100 N·m, Q1 = 8 L / min; when 100 N·m < M ≤ 150 N·m, Q1 = 12 L / min; when 150 N·m < M ≤ 250 N·m, Q1 = 16 L / min; when M > 250 N·m, Q1 = 18 L / min.

[0089] In the case of S1 > 8000 rpm:

[0090] When M ≤ 50 N·m, Q1 = 8 L / min; when 50 N·m < M ≤ 100 N·m, Q1 = 12 L / min; when 100 N·m < M ≤ 200 N·m, Q1 = 16 L / min; when M > 200 N·m, Q1 = 18 L / min.

[0091] For example, in the case of S1 = 7000 rpm and M = 135.8 N·m, the value of Q1 is 12 L / min.

[0092] Step S22: Obtain the lubrication flow rate Q2 of the differential according to the motor driving speed S1.

[0093] Preferably, the relationship between the motor driving speed S1 and the value of the lubrication flow rate Q2 of the differential is as follows:

[0094] 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; when S1 ≥ 18000 rpm, Q2 = 18 L / min.

[0095] For example, when S1 = 7000 rpm, the value of Q2 is 10 L / min.

[0096] Step S23: Obtain the protection flow rate Q3 of the differential according to the wheel speed difference S2, where the wheel speed difference S2 is the difference in rotational speed between the outer wheel and the inner wheel connected to the differential.

[0097] Preferably, the relationship between the wheel speed difference S2 and the value of the protection flow rate Q3 of the differential is as follows:

[0098] When 30 rpm < S2 ≤ 50 rpm, Q3 = 10 L / min; when 50 rpm < S2 ≤ 70 rpm, Q3 = 14 L / min; when S2 > 70 rpm, Q3 = 18 L / min.

[0099] For example, when S2 = 48 rpm, the value of Q3 is 10 L / min.

[0100] Step S24: Obtain the first compensation flow rate Q4 according to the oil temperature T.

[0101] Preferably, the relationship between the oil temperature T and the value of the first compensation flow rate Q4 is as follows:

[0102] When -30°C ≤ T < 10°C, Q4 = 0 L / min; when 10°C ≤ T < 30°C, Q4 = 1 L / min; when 30°C ≤ T < 80°C, Q4 = 1.5 L / min; when 80°C ≤ T < 120°C, Q4 = 2 L / min; when T ≥ 120°C, Q4 = 3 L / min.

[0103] For example, when T = 80°C, the value of Q4 is 2 L / min.

[0104] It should be noted that the calculation order of Q1, Q2, Q3, and Q4 is not sequential, that is, the execution order of Step S21, Step S22, Step S23, and Step S24 is not sequential.

[0105] Step S25: Add 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 to the first compensation flow rate Q4 to obtain the required flow rate Qreq of the oil pump; that is, Qreq = max(Q1, Q2, Q3) + Q4.

[0106] For example, when Q1 = 12 L / min, Q2 = 10 L / min, Q3 = 10 L / min, and Q4 = 2 L / min, Qreq = 14 L / min.

[0107] More specifically, the steps to obtain the actual flow rate Qact of the oil pump are as follows:

[0108] Step S11: Obtain the driving speed S3 of the oil pump, the displacement V of the oil pump, and the volumetric efficiency η of the oil pump.

[0109] In step S11, the maximum value between the mechanical driving speed S4 and the motor driving speed S1 is the driving speed S3 of the oil pump. The displacement V of the oil pump can be obtained through calculation based on the model parameters of the selected oil pump.

[0110] In addition, in step S11, it also includes step S111: Obtain the volumetric efficiency η of the oil pump according to the oil temperature T; among them, the oil temperature T can be measured and obtained through a temperature sensor.

[0111] Preferably, the relationship between the value of the oil temperature T and the volumetric efficiency η of the oil pump is as follows:

[0112] When -30°C ≤ T < 30°C, η = 0.9%; when 30°C ≤ T < 80°C, η = 0.85%; when 80°C ≤ T < 120°C, η = 0.7%; when T ≥ 120°C, η = 0.6%.

[0113] For example, in the case of T = 80°C, the value of η is 0.7%.

[0114] Step S12: Obtain the second compensation flow rate Q5 according to the cumulative working duration t of the oil pump; among them, the cumulative working duration 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.

[0115] Preferably, the relationship between the cumulative working duration t of the oil pump and the value of the second compensation flow rate Q5 is as follows:

[0116] When 5000h ≤ t < 15000h, Q5 = 0.1L / min; when 15000h ≤ t < 25000h, Q5 = 0.15L / min; when t ≥ 25000h, Q5 = 0.2L / min.

[0117] For example, in the case of t = 40000h, the value of Q5 is 0.2L / min.

[0118] Step S13: The sum of the product of the driving speed S3 of the oil pump, the displacement V of the oil pump, and the volumetric efficiency η and the second compensation flow rate Q5 is the actual flow rate Qact of the oil pump, that is, Qact = S3 × V × η + Q5.

[0119] It should be noted that the corresponding relationships between the values of different flow rates and each parameter can be obtained based on software simulation and / or practical experience, or can be obtained through actual measurement.

[0120] The dual-drive oil pump control method according to the present invention is applied to a dual-drive oil pump system of a hybrid transmission in which a mechanical drive and an electric drive are connected to the same oil pump. Under different working conditions, the required flow rate and the actual flow rate for cooling and lubrication during the operation of the hybrid transmission are calculated in real time, and combined with the rotational speed of the mechanical drive, the optimal rotational speed of the DC motor is obtained, improving the efficiency of the hybrid transmission and effectively reducing the drive cost.

[0121] The second aspect of the present invention provides a dual-drive oil pump system for a hybrid transmission, which includes a mechanical drive 1, an electric drive 2, an oil pump 3, and a connection assembly.

[0122] Hereinafter, the specific structures of the above components of the dual-drive oil pump control method according to the present embodiment will be described.

[0123] In the present embodiment, as Figure 3 and Figure 4 shown, both the mechanical drive 1 and the electric drive 2 are connected to the oil pump 3. Among them, the kinetic energy of the mechanical drive 1 can come from the input shaft of the hybrid transmission, and the kinetic energy of the electric drive 2 can come from a DC motor.

[0124] Preferably, the oil pump 3 is an internal gear pump with a single input end.

[0125] Specifically, in the present embodiment, as Figure 3 and Figure 4 shown, the connection 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. Among them, the first input shaft 4, the second input shaft 5, and the output shaft 6 can be arranged parallel to each other, and the output shaft 6 is connected to the input end of the oil pump 3.

[0126] Furthermore, in the present embodiment, as Figure 3 and Figure 4 shown, the clutch assembly includes a first one-way clutch member 7 provided between the first input shaft 4 and the output shaft 6 and a second one-way clutch member 8 provided between the second input shaft 5 and the output shaft 6. The first one-way clutch member 7 and the second one-way clutch member 8 can only rotate in one direction and are locked in the relative rotation direction, so that the kinetic energy of the mechanical drive 1 can only be transmitted from the first input shaft 4 to the output shaft 6 and cannot be transmitted to the second input shaft 5, and the kinetic energy of the electric drive 2 can only be transmitted from the second input shaft 5 to the output shaft 6 and cannot be transmitted to the first input shaft 4.

[0127] Specifically, both the first one-way clutch 7 and the second one-way clutch 8 can adopt one-way clutches. A one-way clutch includes an inner ring, an outer ring, a cage, and wedges. When the inner ring is fixed, the outer ring can rotate clockwise. At this time, the wedges will not lock, allowing the inner ring to rotate freely. When the outer ring rotates counterclockwise, the wedges lock to prevent the outer ring from continuing to rotate. One-way clutches are widely used, inexpensive, and do not require additional control, thus being able to reduce the cost of the hybrid transmission.

[0128] In this embodiment, the first one-way clutch 7 and the second one-way clutch 8 have the same rotation direction.

[0129] Furthermore, in this embodiment, as Figure 3 and Figure 4 shown, the connection assembly further includes a gear set. The gear set includes 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 meshed with the driven wheel 93, and the first driving wheel 91 and the second driving wheel 92 are not meshed with each other to achieve power transmission. The first driving wheel 91 and the second driving wheel 92 can be arranged at both ends in the radial direction of the driven wheel 93. The first one-way clutch 7 is arranged between the first driving wheel 91 and the first input shaft 4, and the second one-way clutch 8 is arranged between the second driving wheel 92 and the second input shaft 5. The driven wheel 93 is fixed to the output shaft 6. In this way, when the first driving wheel 91 rotates, the second input shaft 5 does not rotate; when the second driving wheel 92 rotates, the first input shaft 4 does not rotate.

[0130] Furthermore, in this embodiment, as Figure 3 and Figure 4 shown, the first input shaft 4 is connected to the inner ring of the first one-way clutch 7 by interference fit, and the first driving wheel 91 is connected to the outer ring of the first one-way clutch 7 by interference fit. Preferably, the second input shaft 5 is connected to the inner ring of the second one-way clutch 8 by interference fit, and the second driving wheel 92 is connected to the outer ring of the second one-way clutch 8 by interference fit.

[0131] Specifically, when the mechanical drive 1 works, it drives the first input shaft 4 to rotate clockwise, and then the first input shaft 4 drives the first one-way clutch and drives the first driving wheel 91 to rotate clockwise, so that the driven wheel 93 meshed 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. Therefore, the second input shaft 5 has no rotation tendency.

[0132] More specifically, when the motor drive 2 is operating, it drives the second input shaft 5 to rotate clockwise. Subsequently, the second input shaft 5 drives the second one-way clutch and drives the second driving wheel 92 to rotate clockwise, causing the driven wheel 93 engaged with the second driving wheel 92 to drive the output shaft 6 to rotate counterclockwise. At this time, the driven wheel 93 also drives the first driving wheel 91 to rotate clockwise. However, under the action of the first one-way clutch member 7, the first driving wheel 91 cannot drive the first input shaft 4 to rotate clockwise. Therefore, the first input shaft 4 has no tendency to rotate.

[0133] The dual-drive oil pump system for a hybrid transmission according to the present invention has a simple structure and low cost. By using the first one-way clutch member and the second one-way clutch member, the mechanical drive and the motor drive are connected to the same oil pump without additional control, enabling the dual-drive oil pump system to effectively reduce the cost of the hybrid transmission.

[0134] Finally, it should be noted that the above-described embodiments are only specific embodiments of the present application, used to illustrate the technical solutions of the present application, rather than limiting them. The protection scope of the present application is not limited thereto. Although the present application has been described in detail with reference to the foregoing embodiments, those of ordinary skill in the art should understand that any person skilled in the art within the technical scope disclosed by the present application can still modify the technical solutions described in the foregoing embodiments, or can easily conceive of changes, or perform equivalent replacements for some of the technical features; and these modifications, changes, or replacements do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present application, and should all be covered within the protection scope of the present application. Therefore, the protection scope of the present application should be determined by the protection scope of the claims.

Claims

1. A dual-drive oil pump control method is applied to a dual-drive oil pump system of a hybrid transmission in which mechanical drive and motor drive are connected to the same oil pump. It is characterized in that, Including: Obtain the heat dissipation flow rate Q1 of the motor according to the power of the motor, obtain the lubrication flow rate Q2 of the differential according to the motor driving speed S1, obtain the protection flow rate Q3 of the differential according to the wheel speed difference S2, obtain the first compensation flow rate Q4 and the volumetric efficiency η of the oil pump according to the oil temperature T, and obtain the second compensation flow rate Q5 according to the cumulative working duration t of the oil pump; The sum of 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 and the first compensation flow rate Q4 is the required flow rate Qreq of the oil pump; The sum of 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 and the second compensation flow rate Q5 is the actual flow rate Qact of the oil pump; When the actual flow rate Qact ≥ the required flow rate Qreq, the motor does not start and the mechanical drive starts; when the actual flow rate Qact < the required flow rate Qreq, the motor starts to the preset speed.

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

3. The dual-drive oil pump control method according to claim 1, characterized in that 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; When S1≥18000 rpm, Q2 = 18 L / min.

4. The dual-drive oil pump control method according to claim 1, wherein When 30 rpm < S2 ≤ 50 rpm, Q3 = 10 L / min; When 50 rpm < S2 ≤ 70 rpm, Q3 = 14 L / min; When S2 > 70 rpm, Q3 = 18 L / min.

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

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

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

8. The dual-drive oil pump control method according to claim 1, characterized in that The maximum value of the mechanical drive speed S4 and the motor drive speed S1 is the oil pump drive speed S3; and / or, the preset speed is greater than the mechanical drive speed S4.

9. A dual-drive oil pump system for a hybrid transmission, based on the dual-drive oil pump control method according to any one of claims 1 to 8, characterized in that, Comprising: Mechanical drive, motor drive, oil pump and connection components, the mechanical drive and the motor drive are both connected to the oil pump; The connection components include a first input shaft connected to the mechanical drive, a second input shaft connected to the motor drive, an output shaft connected to the oil pump and a clutch assembly; The clutch assembly includes a first one-way clutch member disposed between the first input shaft and the output shaft and a second one-way clutch member disposed between the second input shaft and the output shaft; the first one-way clutch member and the second one-way clutch member can only rotate in one direction and are locked in the relative rotation direction, so that the kinetic energy of the mechanical drive can only be transmitted from the first input shaft to the output shaft and cannot be transmitted 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 and cannot be transmitted to the first input shaft.

10. The dual-drive oil pump system for a hybrid transmission according to claim 9, characterized in that, The connection components further include a gear set, the gear set includes a first driving wheel, a second driving wheel and a driven wheel, the first driving wheel and the second driving wheel are respectively engaged with the driven wheel, the first one-way clutch member is disposed between the first driving wheel and the first input shaft, the second one-way clutch member is disposed 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 according to claim 10, characterized in that, The first input shaft is connected with the inner ring of the first one-way clutch by interference fit, and the first driving wheel is connected with the outer ring of the first one-way clutch by interference fit; And / or, the second input shaft is connected with the inner ring of the second one-way clutch by interference fit, and the second driving wheel is connected with the outer ring of the second one-way clutch by interference fit.

12. The dual-drive oil pump system for a hybrid transmission according to claim 9, wherein, The kinetic energy of mechanical drive 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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