Hydraulic system and automobile

Abstract

Provided are a hydraulic system and an automobile. The hydraulic system comprises a power generator (1), a driving motor (2), an electric pump (3), a first oil supply assembly (4), a mechanical pump (5), and a second oil supply assembly (6); the first oil supply assembly (4) is communicated with a first rotor (11) by means of a first pressure valve (41), and is communicated with a second rotor (21) by means of a second pressure valve (42); the output end of the second oil supply assembly (6) is in unidirectional communication with the output end of the first oil supply assembly (4) by means of a third pressure valve (61), and one direction is from the output end of the second oil supply assembly to the output end of the first oil supply assembly.

Description

A hydraulic system and an automobile

[0001] This application claims priority to Chinese Patent Application No. 202420869501.2, filed on April 24, 2024, entitled "A Hydraulic System and Automobile", the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to the field of automotive lubrication and cooling technology, and in particular to a hydraulic system and an automobile. Background Technology

[0003] A car is a means of transportation that uses the coordinated operation of multiple components to enable users to travel.

[0004] A car includes a drive motor, a generator, and an oil pump. The drive motor and generator generate heat when they work, and the oil pump supplies oil to the drive motor and generator for lubrication and cooling.

[0005] In related technologies, in order to maintain the normal operation of generators and drive motors, oil pumps generally consume a lot of energy and are prone to overheating, which can lead to power limitation.

[0006] Summary of the Invention

[0007] This application provides a hydraulic system and an automobile, including the following technical solutions:

[0008] A first aspect of this application provides a hydraulic system comprising a generator, a drive motor, an electric pump, a first oil supply assembly, a mechanical pump, and a second oil supply assembly. The generator includes a first rotor and a first stator. The drive motor includes a second rotor and a second stator. The electric pump supplies oil to the first rotor, the second rotor, and the second stator via the first oil supply assembly. The first oil supply assembly is connected to the first rotor via a first pressure valve and to the second rotor via a second pressure valve. The mechanical pump supplies oil to the first rotor, the second rotor, the second stator, the first stator, and the output end of the first oil supply assembly via the second oil supply assembly. The output end of the second oil supply assembly is connected to the output end of the first oil supply assembly via a third pressure valve, wherein the unidirectional connection refers to the flow from the output end of the second oil supply assembly to the output end of the first oil supply assembly.

[0009] In some embodiments, the first oil supply assembly includes a bypass valve and an oil cooler, the bypass valve connecting the output of the first oil supply assembly to the electric pump; the oil cooler connecting the output of the first oil supply assembly to the electric pump.

[0010] In some embodiments, the first oil supply assembly further includes a first check valve and a second check valve, the first check valve connecting the electric pump and the bypass valve, and connecting the electric pump and the oil cooler, the second check valve connecting the bypass valve and the oil cooler.

[0011] In some embodiments, the second oil supply assembly includes a fourth pressure valve and a regulating valve. The fourth pressure valve is connected to the mechanical pump and the first stator, and is used to allow or prevent the mechanical pump from supplying oil to the first stator. The regulating valve is connected to the mechanical pump and the fourth pressure valve to control the opening degree of the fourth pressure valve.

[0012] In some embodiments, the hydraulic system includes a clutch, and the second oil supply assembly further includes a switching valve that connects the mechanical pump and the clutch.

[0013] In some embodiments, the hydraulic system includes a clutch, and both the first oil supply assembly and the second oil supply assembly are in communication with the clutch.

[0014] In some embodiments, the hydraulic system includes a pressure relief valve located between the third pressure valve and the second oil supply assembly, and connected to the outputs of the third pressure valve and the second oil supply assembly, respectively.

[0015] In some embodiments, when the electric pump and the mechanical pump are running simultaneously, the oil pressure at the output end of the first oil supply component is less than the oil pressure at the output end of the second oil supply component.

[0016] In some embodiments, the hydraulic system includes a controller that is signal-connected to both the electric pump and the mechanical pump.

[0017] The controller is configured to control the oil flow rate of the electric pump and the oil flow rate of the mechanical pump respectively, so that the oil pressure at the output end of the first oil supply component is less than the oil pressure at the output end of the second oil supply component.

[0018] In some embodiments, the controller is signal-connected to the first pressure valve and configured to: control the opening of the first pressure valve such that the ratio of oil flow rate of the first stator to oil flow rate of the first rotor is greater than or equal to 4:1; and / or,

[0019] The controller is signal-connected to the second pressure valve and is configured to control the opening of the second pressure valve so that the ratio of the oil flow rate of the second stator to the oil flow rate of the second rotor is greater than or equal to 4:1.

[0020] A second aspect of this application provides an automobile that includes a hydraulic system as described in the first aspect. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0022] Figure 1 is a schematic diagram of a hydraulic system provided in an embodiment of this application;

[0023] Figure 2 is a schematic diagram of the working condition of the first hydraulic system provided in the embodiment of this application;

[0024] Figure 3 is a schematic diagram of the working condition of the second hydraulic system provided in the embodiment of this application;

[0025] Figure 4 is a schematic diagram of the working status of the third hydraulic system provided in the embodiment of this application;

[0026] Figure 5 is a schematic diagram of the control architecture of a controller provided in an embodiment of this application.

[0027] The reference numerals in the figure indicate:

[0028] 1. Generator; 11. First rotor; 12. First stator;

[0029] 2. Drive motor; 21. Second rotor; 22. Second stator;

[0030] 3. Electric pump;

[0031] 4. First oil supply assembly; 41. First pressure valve; 42. Second pressure valve; 43. Bypass valve; 44. Oil cooler; 45. First check valve; 46. Second check valve;

[0032] 5. Mechanical pumps;

[0033] 6. Second oil supply assembly; 61. Third pressure valve; 62. Fourth pressure valve; 63. Regulating valve; 64. Switch valve;

[0034] 7. Clutch;

[0035] 8. Pressure relief valve;

[0036] 9. Shaft teeth;

[0037] 10. Controller.

[0038] The accompanying drawings illustrate specific embodiments of this application, which will be described in more detail below. These drawings and descriptions are not intended to limit the scope of the concept in any way, but rather to illustrate the concept of this application to those skilled in the art through reference to particular embodiments. Detailed Implementation

[0039] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0040] The directional terms used in the embodiments of this application, such as "up," "down," and "side," are generally based on the relative positions shown in Figure 1. These directional terms are used merely to more clearly describe the relationships between structures, not to describe absolute positions. When the product is placed in different orientations, the positions may change; for example, "up" and "down" may be interchanged.

[0041] Unless otherwise defined, all technical terms used in the embodiments of this application have the same meaning as commonly understood by one of ordinary skill in the art.

[0042] To make the technical solutions and advantages of this application clearer, the embodiments of this application will be described in further detail below with reference to the accompanying drawings.

[0043] The first aspect of this application provides a hydraulic system, as shown in FIG1. ​​The hydraulic system includes a generator 1, a drive motor 2, an electric pump 3, a first oil supply assembly 4, a mechanical pump 5, and a second oil supply assembly 6. The generator 1 includes a first rotor 11 and a first stator 12. The drive motor 2 includes a second rotor 21 and a second stator 22. The electric pump 3 is used to supply oil to the first rotor 11, the second rotor 21, and the second stator 22 via the first oil supply assembly 4. The first oil supply assembly 4 is connected to the first rotor 11 via a first pressure valve 41 and to the second rotor 21 via a second pressure valve 42. The mechanical pump 5 is used to supply oil to the first rotor 11, the second rotor 21, the second stator 22, the first stator 12, and the output end of the first oil supply assembly 4 via the second oil supply assembly 6. The output end of the second oil supply assembly 6 is unidirectionally connected to the output end of the first oil supply assembly 4 via a third pressure valve 61, where unidirectional means from the output end of the second oil supply assembly 6 to the output end of the first oil supply assembly 4. Specifically, the third pressure valve 61 can restrict the flow direction of the oil flowing through the third pressure valve 61, so that it can only flow from the second oil supply assembly 6 to the first oil supply assembly 4, and cannot flow in the opposite direction.

[0044] Understandably, the mechanical pump 5 and the electric pump 3 lubricate and cool the first rotor 11, the second rotor 21, and the second stator 22 by supplying oil to these components. The mechanical pump 5 supplies oil to the first stator 12 through the second oil supply assembly 6, which lubricates and cools the first stator 12.

[0045] Since the oil supplied to the first stator 12 is delivered separately by the electric pump 3 through the second oil supply assembly 6, the independence of lubrication and cooling of the first stator 12 can be improved, thereby improving the rationality of oil distribution in the hydraulic system of this application.

[0046] The first oil supply component 4 is connected to the first rotor 11 through the first pressure valve 41 and to the second rotor 21 through the second pressure valve 42. By controlling the opening of the first pressure valve 41 and the second pressure valve 42, the amount of oil supplied to the first rotor 11 and the second rotor 21 can be reasonably adjusted to avoid excessive oil being supplied to the first rotor 11 and the second rotor 21, thereby reducing oil waste.

[0047] The output end of the second oil supply component 6 is unidirectionally connected to the output end of the first oil supply component 4 through the third pressure valve 61. This facilitates the mechanical pump 5 to supply oil to the first rotor 11, the second rotor 21, and the second stator 22 through the second oil supply component 6, and improves the oil supply sealing performance of the second oil supply component 6. This also allows the user to use the mechanical pump 5 to deliver the driven oil to these components according to actual needs, thereby improving the rationality of oil distribution.

[0048] In related technologies, due to space constraints within the vehicle, oil pumps typically rely on a single port to lubricate multiple components simultaneously. Since these components operate under varying conditions, the port cannot meet the lubrication needs of all components, easily leading to insufficient lubrication and subsequent failure of some parts. Furthermore, maintaining lubrication for multiple components results in higher energy consumption for the oil pump, which generates more heat, potentially limiting the pump's power output.

[0049] In this embodiment, on the one hand, an electric pump 3 delivers oil to the first rotor 11, the second rotor 21, and the second stator 22 to meet their lubrication needs and maintain their normal operation. On the other hand, considering that the generator 1 operates for a short time and the first stator 12 operates at a low temperature, a mechanical pump 5 is used to lubricate and cool it separately through the second oil supply assembly 6. This separates the lubrication and cooling of the first stator 12 from the other three components, allowing for targeted lubrication and cooling of the first stator 12 according to actual needs. This can initially reduce the amount of oil delivered to the first stator 12 and reduce oil waste.

[0050] Furthermore, in the hydraulic system of this application embodiment, the output end of the first oil supply component 4 and the output end of the second oil supply component are also connected to the first rotor 11 through the first pressure valve 41 and to the second rotor 21 through the second pressure valve 42. On the one hand, this can reduce the amount of oil delivered to the first rotor 11 and the second rotor 21 when the oil pressure generated by the electric pump 3 is low, thereby increasing the amount of oil delivered to the second stator 22 and improving the lubrication and cooling efficiency of the second stator 22. On the other hand, it is also beneficial to provide the first rotor 11 and the second rotor 21 with sufficient pressure and quantity of oil, thereby improving the lubrication and cooling effect of the first rotor 11 and the second rotor 21.

[0051] It should be understood that, in the embodiments of this application, both the first oil supply component 4 and the second oil supply component 6 include oil supply pipelines, and the various components in the hydraulic system can be directly connected or connected through oil supply pipelines.

[0052] As shown in Figures 2 to 4, in this embodiment of the application, the hydraulic system has three working states, specifically including:

[0053] 1. As shown in Figure 2. The electric pump 3 is working, while the mechanical pump 5 is not working. The electric pump 3 supplies oil to the first rotor 11, the second rotor 21, and the second stator 22 through the first oil supply assembly 4. The opening degrees of the first pressure valve 41 and the second pressure valve 42 are controlled according to the actual lubrication and cooling needs of each component. The third pressure valve 61 blocks the supply of oil driven by the electric pump 3 to the second oil supply assembly 6.

[0054] 2. As shown in Figure 3, both the electric pump 3 and the mechanical pump 5 are operational. The electric pump 3 supplies oil to the first rotor 11, the second rotor 21, and the second stator 22 via the first oil supply assembly 4. The mechanical pump 5 supplies oil to the first stator 12 via the second oil supply assembly 6, and can also supply oil to the first rotor 11, the second rotor 21, and the second stator 22 via the first oil supply assembly 4 through the third pressure valve 61. The opening degrees of the first pressure valve 41, the second pressure valve 42, and the third pressure valve 61 are controlled according to the actual lubrication and cooling needs of each component. For example, if the amount of oil supplied by the electric pump 3 is sufficient to meet the lubrication and cooling needs of the first rotor 11, the second rotor 21, and the second stator 22, the third pressure valve 61 can be closed, i.e., the opening degree of the third pressure valve 61 can be controlled to zero, so that the mechanical pump 5 supplies oil only to the first stator 12 through the second oil supply assembly 6.

[0055] 3. As shown in Figure 4. The mechanical pump 5 is working, while the electric pump 3 is not working. The mechanical pump 5 supplies oil to the first stator 12 through the second oil supply assembly 6, and simultaneously supplies oil to the first rotor 11, the second rotor 21, and the second stator 22 through the first oil supply assembly 4 via the third pressure valve 61.

[0056] In some embodiments of this application, the first pressure valve 41 can be a one-way valve. This one-way valve not only restricts the direction of flow of the liquid but also limits the flow rate of the liquid. Exemplarily, this one-way valve is specifically a one-way throttle valve.

[0057] In some embodiments of this application, the second pressure valve 42 can be a one-way valve. This one-way valve not only restricts the direction of flow of the liquid but also limits the flow rate of the liquid. Exemplarily, this one-way valve is specifically a one-way throttle valve.

[0058] In some embodiments of this application, the third pressure valve 61 can be a one-way valve. This one-way valve not only restricts the direction of flow of the liquid but also limits the flow rate of the liquid. Exemplarily, this one-way valve is specifically a one-way throttle valve.

[0059] In some embodiments of this application, as shown in FIG1, the hydraulic system may further include a gear 9 and a clutch 7, and the electric pump 3 may also supply oil to the gear 9 and the clutch 7 respectively through the first oil supply component 4, so as to lubricate and cool the gear 9 and the clutch 7.

[0060] In some embodiments of this application, the hydraulic system may further include a structure (not shown in the figure) for recovering and cooling oil, which is connected to the electric pump 3 and the mechanical pump 5 respectively, and can cool the oil that has completed the lubrication and cooling work, and deliver the cooled oil to the mechanical pump 5 and the electric pump 3 respectively.

[0061] In some embodiments of this application, as shown in FIG1, the first oil supply assembly 4 includes a bypass valve 43 and an oil cooler 44. The output end of the first oil supply assembly 4 is connected to the electric pump 3 through the bypass valve 43, and the output end of the first oil supply assembly 4 is also connected to the electric pump 3 through the oil cooler 44. Specifically, the bypass valve 43 has two interfaces: an inlet and an outlet (not shown in the figure). The electric pump 3 is connected to the inlet of the bypass valve 43, and the output end of the first oil supply assembly 4 is connected to the outlet of the bypass valve 43. The oil cooler 44 also has two interfaces: an inlet and an outlet (not shown in the figure). The electric pump 3 is connected to the inlet of the oil cooler 44, and the output end of the first oil supply assembly 4 is connected to the outlet of the oil cooler 44. Therefore, the bypass valve 43 and the oil cooler 44 are connected in parallel in the hydraulic system.

[0062] Understandably, the bypass valve 43 maintains the oil supply to the first rotor 11, the second rotor 21, and the second stator 22, thus preserving their lubrication and cooling effects. The oil cooler 44 reduces the oil temperature passing through the bypass valve 43, thereby improving the cooling effect on the first rotor 11, the second rotor 21, and the second stator 22. Through the actions of the bypass valve 43 and the oil cooler 44, the first oil supply assembly 4 achieves better lubrication and cooling of the first rotor 11, the second rotor 21, and the second stator 22.

[0063] In some embodiments of this application, as shown in FIG1, the first oil supply assembly 4 further includes a first check valve 45 and a second check valve 46. The first check valve 45 is connected to the electric pump 3 and the bypass valve 43, and is also connected to the electric pump 3 and the oil cooler 44. The second check valve 46 is connected to the bypass valve 43 and the oil cooler 44.

[0064] Specifically, the first check valve 45 has two ports: an inlet and an outlet (not shown in the figure). The inlet of the first check valve 45 is connected to the electric pump 3, and the outlet of the first check valve 45 is connected to the inlet of the bypass valve 43 and the inlet of the oil cooler 44, respectively. The second check valve 46 has two ports: an inlet and an outlet (not shown in the figure). The inlet of the second check valve 46 is connected to the outlet of the bypass valve 43 and the outlet of the oil cooler 44, respectively, and the outlet of the second check valve 46 is connected to the output end of the first oil supply assembly 4.

[0065] Understandably, the first check valve 45 can prevent oil from flowing back into the electric pump 3 when the oil cooler 44 and bypass valve 43 become blocked, thus reducing the impact on the electric pump 3. The second check valve 46 can prevent oil driven by the second oil supply assembly 6 from flowing back into the bypass valve 43 and oil cooler 44, which helps to improve the operational independence between the first oil supply assembly 4 and the second oil supply assembly 6.

[0066] In some embodiments of this application, as shown in FIG1, the second oil supply assembly 6 includes a fourth pressure valve 62 and a regulating valve 63. The fourth pressure valve 62 and the regulating valve 63 are respectively connected to the mechanical pump 5. The fourth pressure valve 62 is used to supply oil to the first stator 12. The regulating valve 63 is connected to the fourth pressure valve 62 to control the opening degree of the fourth pressure valve 62.

[0067] In the hydraulic system provided in this embodiment, the mechanical pump 5 delivers oil to the first stator 12 via the fourth pressure valve 62, thus providing lubrication and cooling for the first stator 12. The fourth pressure valve 62 and the regulating valve 63 are connected in parallel, working together to achieve real-time control of the oil pressure in the second oil supply assembly 6. In one example, the regulating valve 63 controls the fourth pressure valve 62; by adjusting the opening of the fourth pressure valve 62, the oil quantity in the second oil supply assembly 6 can be adjusted. In another example, the regulating valve 63 and the fourth pressure valve 62 are independent. When the opening of the regulating valve 63 changes, the oil quantity in its circuit changes, which in turn causes a change in the oil quantity in the circuit of the fourth pressure valve 62, thereby adjusting the oil quantity supplied to the first stator 12 by the second oil supply assembly 6. This helps to ensure that the oil quantity delivered by the second oil supply assembly 6 to the first stator 12 is adapted to the working conditions of the first stator 12, thereby reducing waste and energy consumption associated with lubricating and cooling the first stator 12 under other conditions.

[0068] In some embodiments of this application, as shown in FIG1, the hydraulic system includes a clutch 7, and the second oil supply assembly 6 further includes a switching valve 64, which connects the mechanical pump 5 and the clutch 7. Optionally, the clutch 7 may be the same clutch as the clutch 7 mentioned above that is connected to the first oil supply assembly 4, or it may be a different clutch.

[0069] Understandably, clutch 7 is generally used to transmit and interrupt power, and it generates a lot of heat during operation. The mechanical pump 5 and clutch 7 are connected by the switching valve 64. The mechanical pump 5 can supply clutch 7 with oil of sufficient pressure and flow, thus providing lubrication and cooling for clutch 7.

[0070] In this embodiment, the switching valve 64 can be a two-position three-way proportional valve.

[0071] In this embodiment, the hydraulic system may further include an accumulator (not shown in the figure), which is located between the clutch 7 and the switching valve 64 and is in communication with the switching valve 64. The accumulator can stabilize the oil pressure fluctuations of the clutch 7 and reduce the shocks it is subjected to.

[0072] In some embodiments of this application, as shown in FIG1, the hydraulic system includes a clutch 7, and a first oil supply assembly 4 and a second oil supply assembly 6 are both connected to the clutch 7.

[0073] It is understandable that by connecting the clutch 7 through the first oil supply component 4 and the second oil supply component 6, the hydraulic system of this application can increase the oil supply to the clutch 7, which is beneficial to improving the working condition of the clutch 7.

[0074] In some embodiments of this application, as shown in FIG1, the hydraulic system includes a pressure relief valve 8, which is located between the third pressure valve 61 and the second oil supply assembly 6, and is connected to the output ends of the third pressure valve 61 and the second oil supply assembly 6, respectively.

[0075] Understandably, the pressure relief valve 8 can reduce the situation where the oil pressure generated by the second oil supply assembly 6 is too high and opens the third pressure valve 61. This helps to guide the excess oil generated by the second oil supply assembly 6 to other places, which is conducive to distributing oil according to actual needs and reducing the impact on the first oil supply assembly 4.

[0076] In some embodiments of this application, when the electric pump 3 and the mechanical pump 5 operate simultaneously, the oil pressure at the output end of the first oil supply assembly 4 is always lower than the oil pressure at the output end of the second oil supply assembly 6. This not only helps reduce the amount of oil supplied to the first stator 12, but also allows for simultaneous lubrication and cooling of the drive motor 2 and the generator 1 as needed, thereby reducing energy consumption and ensuring that all components can maintain normal operation.

[0077] Moreover, the oil pressure at the output end of the first oil supply component 4 is lower than the oil pressure at the output end of the second oil supply component 6, which is beneficial for the pressurized oil generated by the mechanical pump 5 to be delivered to the first rotor 11, the second rotor 21 and the second stator 22 through the third pressure valve 61, thereby improving the lubrication and cooling effect on the above three components.

[0078] In some embodiments of this application, by selecting electric pump 3 and mechanical pump 5 with different rated flow rates, the oil pressure at the output end of the first oil supply component 4 can be made lower than the oil pressure at the output end of the second oil supply component 6.

[0079] For example, when selecting the electric pump 3 and the mechanical pump 9 for the hydraulic system, an electric pump with a relatively small rated flow rate and a mechanical pump with a relatively large rated flow rate can be selected. Therefore, when the hydraulic system is running, with both the electric pump and the mechanical pump operating at their rated conditions, the oil flow rate provided by the electric pump is naturally less than that provided by the mechanical pump, and consequently, the oil pressure at the output end of the first oil supply component 4 is naturally less than the oil pressure at the output end of the second oil supply component 6.

[0080] In some other embodiments of this application, the oil flow rate output by the electric pump and the oil flow rate output by the mechanical pump can also be controlled by a control device, thereby achieving the effect that the oil pressure at the output end of the first oil supply component 4 is less than the oil pressure at the output end of the second oil supply component 6.

[0081] For example, as shown in FIG5, the hydraulic system further includes a controller 10, which is signal-connected to the electric pump 3 and the mechanical pump 5 respectively, thereby controlling the operation of the electric pump 3 and the mechanical pump 5. Specifically, the controller 10 is configured to control the oil flow rate output by the electric pump 3 and the oil flow rate output by the mechanical pump 5 respectively, so that the oil pressure at the output end of the first oil supply component 4 is always kept lower than the oil pressure at the output end of the second oil supply component 6.

[0082] In some embodiments of this application, the controller 10 is also signal-connected to the first pressure valve 41 and configured to control the opening of the first pressure valve 41 so that the ratio of the oil flow rate of the second stator 22 to the oil flow rate of the second rotor 21 is greater than or equal to 4:1.

[0083] Understandably, the second stator 22 and the second rotor 21 are the working components of the drive motor 2, and both operate for extended periods. The second stator 22 uses a larger oil flow rate for lubrication, which helps it maintain a relatively stable working state. Meanwhile, the second rotor 21 uses a smaller oil flow rate, which helps improve the rationality of oil distribution.

[0084] In this embodiment, the oil flow rate of the second stator 22 refers to the oil flow rate received by the second stator 22 when the second stator 22 and the second rotor 21 are lubricated simultaneously.

[0085] In this embodiment, the oil flow rate of the second rotor 21 refers to the oil flow rate received by the second rotor 21 when the second stator 22 and the second rotor 21 are lubricated simultaneously.

[0086] In some embodiments of this application, the controller 10 is also signal-connected to the second pressure valve 42 and configured to control the opening of the second pressure valve 42 so that the ratio of the oil flow rate of the first stator 12 to the oil flow rate of the first rotor 11 is greater than or equal to 4:1.

[0087] It is understandable that the first stator 12 and the first rotor 11 are working components of the generator 1, and their working time is relatively short. The first stator 12 uses a larger oil flow rate for lubrication, which is conducive to maintaining a relatively stable working state. At the same time, the first rotor 11 has a smaller oil flow rate, which is conducive to improving the rationality of oil distribution.

[0088] In this embodiment, the oil flow rate of the first stator 22 refers to the oil flow rate received by the first stator 22 when the first stator 22 and the first rotor 21 are lubricated at the same time.

[0089] In this embodiment, the oil flow rate of the first rotor 21 refers to the oil flow rate received by the first rotor 21 when the first stator 22 and the first rotor 21 are lubricated at the same time.

[0090] In some embodiments of this application, as shown in FIG5, the controller 10 is also connected to at least one of the following valve signals: first pressure valve 41, second pressure valve 42, third pressure valve 61, fourth pressure valve 62, regulating valve 63, switching valve 64, bypass valve 43, and pressure relief valve 8, thereby controlling the opening degree of the corresponding valve.

[0091] The controller 10 enables automated control of the opening degree of each valve, which allows the hydraulic system to have high flexibility and precise control capabilities, accurately determine the oil demand and supply status of each component during the operation of the hydraulic system, and meet the demand in a timely manner.

[0092] In some other embodiments of this application, as shown in FIG5, the opening degree of at least one of the first pressure valve 41, the second pressure valve 42, the third pressure valve 61, the fourth pressure valve 62, the regulating valve 63, the switching valve 64, the bypass valve 43, and the pressure relief valve 8 can also be manually controlled, thereby realizing flexible adjustment according to actual needs and reducing system costs.

[0093] Referring again to Figure 5, in this embodiment, the controller 10 can also be signal-connected to the oil cooler 44 to control the start and stop of the oil cooler 44, as well as the cooling temperature of the oil cooler 44; alternatively, the oil cooler 44 can also be manually controlled. Therefore, this avoids overuse of the oil cooler 44 in scenarios where there is no cooling requirement, reducing system energy consumption.

[0094] A second aspect of this application provides an automobile that includes a hydraulic system as described in the above embodiments.

[0095] It is understood that, due to the use of the hydraulic system in the above embodiments, the automobile of this application has the same technical effects as the hydraulic system described above, and will not be repeated here.

[0096] In this embodiment of the application, the vehicle may be a hybrid vehicle.

[0097] In some embodiments of this application, the vehicle includes a clutch 7 and an engine, wherein a second oil supply assembly 6 is capable of supplying oil to the clutch 7, and the engine is drive-connected to a mechanical pump 5. The vehicle has the following five modes, specifically including:

[0098] 1. Pure electric mode.

[0099] Electric pump 3 operates, while mechanical pump 5 does not. Electric pump 3 supplies oil to the first rotor 11, second rotor 21, second stator 22, and clutch 7 via the first oil supply assembly 4. The third pressure valve 61 blocks the supply of oil driven by electric pump 3 to the second oil supply assembly 6.

[0100] 2. Series mode.

[0101] Electric pump 3 and mechanical pump 5 operate. Electric pump 3 supplies oil to first rotor 11, second rotor 21, second stator 22 and clutch 7 through first oil supply assembly 4. Mechanical pump 5 supplies oil to first stator 12 through second oil supply assembly 6, and supplies oil to first rotor 11, second rotor 21, second stator 22 and clutch 7 through first oil supply assembly 4 via third pressure valve 61.

[0102] 3. Parallel mode.

[0103] Electric pump 3 and mechanical pump 5 operate. Electric pump 3 supplies oil to first rotor 11, second rotor 21, second stator 22 and clutch 7 through first oil supply assembly 4. Mechanical pump 5 supplies oil to first stator 12 through second oil supply assembly 6, and supplies oil to first rotor 11, second rotor 21, second stator 22 and clutch 7 through first oil supply assembly 4 via third pressure valve 61, and also supplies oil to clutch 7 through second oil supply assembly 6.

[0104] 4. Engine direct drive mode.

[0105] Mechanical pump 5 is operational, while electric pump 3 is not. Mechanical pump 5 supplies oil to the first stator 12 via the second oil supply assembly 6. Simultaneously, it supplies oil to the first rotor 11, second rotor 21, second stator 22, and clutch 7 via the first oil supply assembly 4 through the third pressure valve 61.

[0106] 5. Reverse mode.

[0107] Electric pump 3 operates, while mechanical pump 5 does not. Electric pump 3 supplies oil to the first rotor 11, second rotor 21, second stator 22, and clutch 7 via the first oil supply assembly 4. The third pressure valve 61 blocks the flow of oil driven by electric pump 3 to the second oil supply assembly 6.

[0108] In this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance. The term "multiple" refers to two or more unless otherwise expressly defined.

[0109] Other embodiments of this application will readily occur to those skilled in the art upon consideration of the specification and practice of the application disclosed herein. This application is intended to cover any variations, uses, or adaptations of this application that follow the general principles of this application and include common knowledge or customary techniques in the art not disclosed herein. The specification and examples are to be considered exemplary only.

[0110] It should be understood that this application is not limited to the precise structure described above and shown in the accompanying drawings, and various modifications and changes can be made without departing from its scope. The scope of this application is limited only by the appended claims.

Claims

1. A hydraulic system, wherein, The hydraulic system includes a generator (1), a drive motor (2), an electric pump (3), a first oil supply assembly (4), a mechanical pump (5), and a second oil supply assembly (6), wherein, The generator (1) includes a first rotor (11) and a first stator (12); The drive motor (2) includes a second rotor (21) and a second stator (22); The electric pump (3) is used to supply oil to the first rotor (11), the second rotor (21) and the second stator (22) through the first oil supply assembly (4); The first oil supply assembly (4) is connected to the first rotor (11) through the first pressure valve (41) and to the second rotor (21) through the second pressure valve (42); The mechanical pump (5) is used to supply oil to the output end of the first rotor (11), the second rotor (21), the second stator (22), the first stator (12) and the first oil supply assembly (4) through the second oil supply assembly (6); The output end of the second oil supply component (6) is connected in one direction to the output end of the first oil supply component (4) through the third pressure valve (61). The one-way connection refers to the connection from the output end of the second oil supply component (6) to the output end of the first oil supply component (4).

2. The hydraulic system according to claim 1, wherein, The first oil supply assembly (4) includes a bypass valve (43) and an oil cooler (44). The bypass valve (43) connects the output end of the first oil supply assembly (4) and the electric pump (3); The oil cooler (44) is connected to the output end of the first oil supply assembly (4) and the electric pump (3).

3. The hydraulic system according to claim 2, wherein, The first oil supply assembly (4) also includes a first check valve (45) and a second check valve (46). The first check valve (45) connects the electric pump (3) and the bypass valve (43), and also connects the electric pump (3) and the oil cooler (44); The second check valve (46) connects the bypass valve (43) and the oil cooler (44).

4. The hydraulic system according to claim 1, wherein, The second oil supply assembly (6) includes a fourth pressure valve (62) and a regulating valve (63). The fourth pressure valve (62) connects the mechanical pump (5) and the first stator (12). The fourth pressure valve (62) is used to allow or prevent the mechanical pump (5) from supplying oil to the first stator (12); The regulating valve (63) connects the mechanical pump (5) and the fourth pressure valve (62) to control the opening degree of the fourth pressure valve (62).

5. The hydraulic system according to claim 1, wherein, The hydraulic system includes a clutch (7), and the second oil supply assembly (6) further includes a switching valve (64) that connects the mechanical pump (5) and the clutch (7).

6. The hydraulic system according to claim 1, wherein, The hydraulic system includes a clutch (7), and the first oil supply component (4) and the second oil supply component (6) are both connected to the clutch (7).

7. The hydraulic system according to claim 1, wherein, The hydraulic system includes a pressure relief valve (8), which is located between the third pressure valve (61) and the second oil supply assembly (6), and is connected to the output ends of the third pressure valve (61) and the second oil supply assembly (6), respectively.

8. The hydraulic system according to claim 1, wherein, When the electric pump (3) and the mechanical pump (5) are running simultaneously, the oil pressure at the output end of the first oil supply component (4) is less than the oil pressure at the output end of the second oil supply component (6).

9. The hydraulic system according to claim 8, wherein, The hydraulic system includes a controller (10), which is signal-connected to the electric pump (3) and the mechanical pump (5), respectively. The controller (10) is configured to control the oil flow rate output by the electric pump (3) and the oil flow rate output by the mechanical pump (5) respectively, so that the oil pressure at the output end of the first oil supply component (4) is less than the oil pressure at the output end of the second oil supply component (6).

10. The hydraulic system according to claim 9, wherein, The controller (10) is signal-connected to the first pressure valve (41) and is configured to control the opening of the first pressure valve (41) so that the ratio of the oil flow rate of the first stator (12) to the oil flow rate of the first rotor (11) is greater than or equal to 4:

1.

11. The hydraulic system according to claim 9, wherein, The controller (10) is signal-connected to the second pressure valve (42) and is configured to control the opening of the second pressure valve (42) so that the ratio of the oil flow rate of the second stator (22) to the oil flow rate of the second rotor (21) is greater than or equal to 4:

1.

12. A type of automobile, wherein, The vehicle includes a hydraulic system as described in any one of claims 1 to 11.

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