Cooling and lubrication system and hybrid transmission

Abstract

This application relates to the field of vehicle technology and discloses a cooling and lubrication system and a hybrid transmission. The cooling and lubrication system includes a valve sleeve, a valve core, an oil tank, and an oil cooler. The valve sleeve has a chamber, a first liquid flow channel, and a second liquid flow channel. The oil tank is connected to the inlet end of the oil cooler via the first liquid flow channel and to the outlet end of the oil cooler via the second liquid flow channel. The valve core is at least partially located in the chamber and is movably connected to the valve sleeve. A gap exists between the first end of the valve core and the end wall of the chamber to form a pressure chamber, which is connected to the oil tank. The oil pressure in the pressure chamber is related to the temperature of the lubricating oil in the oil tank. The cooling and lubrication system and hybrid transmission provided by this application can adaptively adjust the cooling and lubrication oil circuit based on the temperature of the lubricating oil itself, thereby improving the working efficiency of the hybrid transmission.

Description

Technical Field

[0001] This application relates to the field of vehicle technology, specifically to a cooling and lubrication system and a hybrid transmission. Background Technology

[0002] A hybrid transmission is a drive system that couples the power of an engine and an electric motor in a certain way, enabling speed and torque changes. To ensure the normal operation of a hybrid transmission, a cooling and lubrication system is often needed to supply lubricating oil to the electric motor and other cooling components in the transmission for forced cooling or lubrication.

[0003] In related technologies, the cooling and lubrication system is usually controlled by solenoid valves to open or close the oil circuit or change the oil circuit, which is costly. In addition, the lubricating oil in the cooling and lubrication system needs to pass through the oil cooler to be cooled before being delivered to the motor, regardless of the temperature. This results in low working efficiency of the hybrid transmission. Summary of the Invention

[0004] In view of this, this application provides a cooling and lubrication system and a hybrid transmission that can adaptively adjust the cooling and lubrication circuit based on the temperature of the lubricating oil itself, thereby improving the working efficiency of the hybrid transmission.

[0005] Specifically, this application includes the following technical solutions:

[0006] The first aspect of this application provides a cooling and lubrication system, which includes: a valve sleeve, a valve core, an oil tank, and an oil cooler;

[0007] The valve sleeve has a chamber, a first liquid flow channel and a second liquid flow channel inside. The oil tank is connected to the inlet end of the oil cooler through the first liquid flow channel and the oil tank is connected to the outlet end of the oil cooler through the second liquid flow channel.

[0008] The valve core is at least partially located within the chamber and is movably connected to the valve sleeve. A gap exists between the first end of the valve core and the end wall of the chamber to form a pressure chamber, which is in communication with the oil tank.

[0009] When the oil pressure in the pressure chamber is lower than a first set value, the valve core is in a first position, so that the first liquid flow channel is opened and the second liquid flow channel is closed; when the oil pressure in the pressure chamber is not lower than a second set value, the valve core moves to a second position away from the end wall of the chamber, so that the first liquid flow channel is closed and the second liquid flow channel is opened, wherein the oil pressure in the pressure chamber is related to the temperature of the lubricating oil in the oil tank.

[0010] In one implementation of this application embodiment, the cooling and lubrication system further includes an elastic element and a fixing plate;

[0011] One end of the elastic element is connected to the fixed plate, and the other end is connected to the second end of the valve core, and is used to drive the valve core to move toward the end wall of the chamber, with the first end and the second end opposite to each other.

[0012] In one implementation of this application, two first annular grooves are formed on the inner sidewall of the chamber. The two first annular grooves are arranged at intervals along the axial direction of the valve sleeve. Each first annular groove is provided with a first annular protrusion to divide the first annular groove into a first sub-groove and a second sub-groove. The two first sub-grooves are respectively connected to the oil tank. Among the two second sub-grooves, the second sub-grooves closer to the pressure chamber are connected to the inlet end of the oil cooler, and the second sub-grooves farther from the pressure chamber are connected to the outlet end of the oil cooler.

[0013] Two second annular grooves are formed on the outer wall of the valve core. The two second annular grooves are arranged at intervals along the axial direction of the valve core. When one of the two first annular protrusions, which is closer to the pressure chamber, faces the second annular groove that is closer to the pressure chamber, the first liquid flow channel is opened. When the other first annular protrusion faces the second annular groove that is farther away from the pressure chamber, the second liquid flow channel is opened.

[0014] In one implementation of this application, one of the two second annular grooves, which is farther from the pressure chamber, has a second annular protrusion. The side of the second annular protrusion facing the inner wall of the chamber has a first inclined surface. The first inclined surface is inclined such that the side farther from the pressure chamber is farther from the central axis of the valve core.

[0015] In one implementation of this application, the end face of the first end partially protrudes towards the second end away from the valve core to form a boss. The side of the boss away from the second end is configured to abut against the end wall of the chamber to form the pressure chamber between the boss and the inner wall of the chamber. The first end is opposite to the second end.

[0016] In one implementation of this application, the sidewall of the boss includes a second inclined surface, and the second inclined surface is inclined such that the closer it is to the end wall of the chamber, the closer it is to the central axis of the valve core.

[0017] In one implementation of this application, a third annular groove is provided on the inner sidewall of the chamber, and the third annular groove is close to the end wall of the chamber;

[0018] When the boss abuts against the end wall of the chamber, the boss is at least partially located within the third annular groove.

[0019] In one implementation of this application, the cooling and lubrication system further includes: an oil supply pipeline, an oil supply pump, and an overflow valve;

[0020] The oil supply pipeline includes a main oil line, three branch oil lines, and a first bypass oil line. One end of the main oil line is connected to the oil tank, and the other end is connected to each of the three branch oil lines. The oil supply pump is installed on the main oil line. The three branch oil lines are respectively connected to the first liquid flow channel, the second liquid flow channel, and the pressure chamber. One end of the first bypass oil line is connected to the inlet end of the oil supply pump, and the other end is connected between the outlet end of the oil supply pump and the three branch oil lines. The overflow valve is installed on the first bypass oil line, and the inlet end of the overflow valve is connected to the outlet end of the oil supply pump.

[0021] In one implementation of this application, the oil supply pipeline further includes a second bypass oil passage, and the cooling and lubrication system further includes a one-way valve;

[0022] One end of the second bypass oil circuit is connected to the inlet end of the oil supply pump, and the other end is connected between the outlet end of the oil supply pump and the three branch oil circuits. The one-way valve is installed on the second bypass oil circuit, and the inlet end of the one-way valve is connected to the inlet end of the oil supply pump.

[0023] A second aspect of this application provides a hybrid transmission including the aforementioned cooling and lubrication system.

[0024] The beneficial effects of the technical solutions provided in this application include at least the following:

[0025] In the cooling and lubrication system provided in this application embodiment, the valve core is located inside the valve sleeve and can move along the extension direction of the cavity inside the valve sleeve. The oil tank can directly supply oil to the pressure chamber formed between the valve core and the end wall of the cavity. When the temperature of the lubricating oil is high, resulting in a lower viscosity of the lubricating oil, the oil pressure inside the pressure chamber will decrease accordingly. At this time, the first liquid flow channel opens, so that the oil tank can supply lubricating oil to the oil cooler through the first liquid flow channel. When the temperature of the lubricating oil is low, resulting in a higher viscosity of the lubricating oil, the oil pressure inside the pressure chamber will increase accordingly, driving the valve core to move away from the end wall of the cavity until the second liquid flow channel is opened. Thus, the oil tank can directly supply lubricating oil to the component to be cooled through the second liquid flow channel without going through the oil cooler. Compared to the cooling and lubrication systems in related technologies, the cooling and lubrication system provided in this application takes into account the oil resistance characteristics of lubricating oil at different temperatures, so that lubricating oil at higher temperatures can flow through the oil cooler for cooling, while lubricating oil at lower temperatures can bypass the oil cooler and flow to the components to be cooled. The hybrid transmission can always operate in a high-efficiency range, thus improving the working efficiency of the hybrid transmission. Attached Figure Description

[0026] 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.

[0027] Figure 1 A first structural schematic diagram of the cooling and lubrication system provided in an embodiment of this application is shown;

[0028] Figure 2 This diagram illustrates the oil flow direction of the cooling and lubrication system provided in this embodiment when the oil is at a high temperature.

[0029] Figure 3 This diagram illustrates the oil flow direction of the cooling and lubrication system provided in this embodiment when the oil is at a low temperature.

[0030] Figure 4 A second structural schematic diagram of the cooling and lubrication system provided in an embodiment of this application is shown;

[0031] Figure 5 A third structural schematic diagram of the cooling and lubrication system provided in an embodiment of this application is shown;

[0032] Figure 6 The diagram shows the oil flow direction of the cooling and lubrication system provided in the embodiment of this application when the oil cooler fails.

[0033] Explanation of reference numerals in the attached figures:

[0034] 1. Valve sleeve; 11. Chamber; 111. Pressure chamber; 112. First annular groove; 1121. First annular protrusion; 1122. First sub-groove; 1123. Second sub-groove; 113. Third annular groove; 114. End wall; 12. First liquid flow channel; 13. Second liquid flow channel;

[0035] 2. Valve core; 21. First end; 211. Boss; 2111. Second inclined surface; 22. Second end; 222. Mounting groove; 23. Second annular groove; 231. Second annular protrusion; 2311. First inclined surface;

[0036] 3. Fuel tank; 4. Oil cooler;

[0037] 5. Elastic components; 6. Fixing plate;

[0038] 7. Oil supply pipeline; 71. Main oil line; 72. Branch oil line; 73. First bypass oil line; 74. Second bypass oil line;

[0039] 8. Oil supply pump; 9. Overflow valve; 10. First check valve; 101. Second check valve.

[0040] 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

[0041] 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. To make the technical solutions and advantages of this application clearer, the noise control method, device, and apparatus will be described in detail below with reference to the accompanying drawings.

[0042] A hybrid transmission is a drive system that couples the power of an engine and an electric motor in a specific way, enabling speed and torque changes. To ensure the proper functioning of a hybrid transmission, a cooling and lubrication system is often needed to supply lubricating oil to the electric motor and other components within the transmission for forced cooling or lubrication. To guarantee the effectiveness of the lubricating oil's cooling or lubrication, the cooling and lubrication system typically includes an oil cooler to cool the lubricating oil before supplying it to the electric motor and other components.

[0043] However, the cooling and lubrication systems in related technologies are usually controlled by solenoid valves to open or close the oil circuit, which is costly. Furthermore, the lubricating oil in the cooling and lubrication system needs to pass through an oil cooler regardless of its temperature, which reduces the efficiency of the hybrid transmission.

[0044] Furthermore, since the viscosity of lubricating oil is related to its temperature, the viscosity of lubricating oil is higher and its fluidity is poorer at low temperatures, while the viscosity of lubricating oil is lower and its fluidity is better at high temperatures. When lubricating oil at low temperatures passes through an oil cooler, its temperature and fluidity may decrease further, thereby affecting the working efficiency of the hybrid transmission.

[0045] In response, this application provides a cooling and lubrication system, such as Figure 1 As shown, the cooling and lubrication system may include: valve sleeve 1, valve core 2, oil tank 3, and oil cooler 4; wherein the valve sleeve 1 has a chamber 11, a first liquid flow channel 12, and a second liquid flow channel 13 inside; the oil tank 3 is connected to the inlet end of the oil cooler 4 through the first liquid flow channel 12, and the oil tank 3 is connected to the outlet end of the oil cooler 4 through the second liquid flow channel 13, so that the oil tank 3 can supply lubricating oil to the oil cooler 4 through the first liquid flow channel 12, while the second liquid flow channel 13 avoids the oil cooler 4, and the oil tank 3 can directly supply lubricating oil to the component 100 to be cooled (e.g., a motor) through the second liquid flow channel 13.

[0046] The valve core 2 is at least partially located within the chamber 11 and is movably connected to the valve sleeve 1. A gap exists between the first end 21 of the valve core 2 and the end wall 114 of the chamber 11 to form a pressure chamber 111, which is connected to the oil tank 3. When the oil pressure in the pressure chamber 111 is lower than a first set value, the valve core 2 is in a first position, so that the first liquid flow channel 12 is opened and the second liquid flow channel 13 is closed. When the oil pressure in the pressure chamber 111 is not lower than a second set value, the valve core 2 moves to a second position away from the end wall 114 of the chamber 11, so that the first liquid flow channel 12 is closed and the second liquid flow channel 13 is opened. The oil pressure in the pressure chamber 111 is related to the temperature of the lubricating oil in the oil tank 3.

[0047] In the cooling and lubrication system provided in this application embodiment, the valve core 2 is located inside the valve sleeve 1 and can move along the extension direction of the chamber 11 inside the valve sleeve 1. The oil tank 3 can directly supply oil to the pressure chamber 111 formed between the valve core 2 and the end wall 114 of the chamber 11. When the temperature of the lubricating oil is high, resulting in a lower viscosity of the lubricating oil, the oil pressure inside the pressure chamber 111 will decrease accordingly. At this time, the first liquid flow channel 12 opens, so that the oil tank 3 can supply lubricating oil to the oil cooler 4 through the first liquid flow channel 12. When the temperature of the lubricating oil is low, resulting in a higher viscosity of the lubricating oil, the oil pressure inside the pressure chamber 111 will increase accordingly, so as to drive the valve core 2 to move away from the end wall 114 of the chamber 11 until the second liquid flow channel 13 is opened. Thus, the oil tank 3 can directly supply lubricating oil to the component 100 to be cooled through the second liquid flow channel 13 without going through the oil cooler 4.

[0048] Therefore, the cooling and lubrication system provided in this application embodiment can adaptively adjust the cooling and lubrication oil path based on the temperature of the lubricating oil itself. Compared with the cooling and lubrication systems in related technologies, the cooling and lubrication system provided in this application takes into account the oil resistance characteristics of the lubricating oil at different temperatures, so that the lubricating oil with a higher temperature can flow through the oil cooler 4 for cooling, while the lubricating oil with a lower temperature can bypass the oil cooler 4 and flow to the components to be cooled, so that the hybrid transmission can operate in the high-efficiency range as soon as possible, thereby improving the working efficiency of the hybrid transmission.

[0049] In one example, such as Figure 2 As shown, when the lubricating oil temperature is high, the viscosity of the lubricating oil is low. At this time, the oil pressure in the pressure chamber 111 is lower than the first set value, which is insufficient to push the valve core 2 to move, thereby keeping the first liquid flow channel 12 open. The lubricating oil in the oil tank 3 flows through the first liquid flow channel 12 to the inlet end of the oil cooler 4, and is cooled in the oil cooler 4 before being delivered to the lubricated parts to be cooled.

[0050] In another example, such as Figure 3 As shown, when the oil temperature is low, the viscosity of the lubricating oil is high. At this time, the oil pressure in pressure chamber 111 is greater than or equal to the second set value, compared to... Figure 2 As shown, the valve core 2 moves away from the end wall 114, causing the second liquid flow channel 13 to open and the first liquid flow channel 12 to close. The lubricating oil at a lower temperature flows directly through the second liquid flow channel 13 to the outlet end of the oil cooler 4, and then directly to the lubricated component to be cooled.

[0051] To improve the stability of the valve core 2 in the first position when the first liquid flow channel 12 is opened and the second position when the second liquid flow channel 13 is opened, and to avoid the problem that the valve core 2 can be easily pushed by oil pressure due to the valve core 2 being maintained solely by the frictional force between the valve core 2 and the valve body 1, in some embodiments of this application, such as Figure 1As shown, the cooling and lubrication system may also include an elastic element 5 and a fixed plate 6; one end of the elastic element 5 is connected to the fixed plate 6, and the other end is connected to the second end 22 of the valve core 2, and is used to drive the valve core 2 to move toward the end wall 114 of the chamber 11, with the first end 21 opposite to the second end 22.

[0052] An elastic element 5 is provided at one end of the valve core 2 away from the end wall 114 of the chamber 11, and the elastic element 5 is connected to the fixed plate 6 which is fixed in position. It provides the valve core 2 with an axial thrust at all times, so as to offset part of the pressure after the lubricating oil enters the pressure chamber 111, and to finely control the opening and closing of the first liquid flow channel 12 and the second liquid flow channel 13. For example, it avoids the pressure generated by the lubricating oil from accidentally pushing the valve core 2 when the oil temperature is moderate or high, so that the lubricating oil with high temperature is not delivered to the lubricated parts to be cooled through the oil cooler 4, thereby reducing the working efficiency of the hybrid transmission.

[0053] Optionally, the elastic element 5 is a spring, such as a compression spring.

[0054] In some embodiments, the second set value may be greater than the first set value. When the valve core 2 is in the first position that maintains the first liquid flow channel 12 open, the elastic member 5 may be in the natural state, so that the oil pressure in the pressure chamber 111 is balanced with the frictional force between the valve core 2 and the valve sleeve 1; or, the elastic member 5 may be in the pre-compressed state, so that the oil pressure in the pressure chamber 111 is balanced with the elastic force (pre-compression force) of the elastic member 5. When the temperature of the lubricating oil decreases, causing the oil pressure in the pressure chamber 111 to exceed the first set value, the friction between the valve core 2 and the valve sleeve 1 or the pre-compression force of the elastic element 5 can be overcome, pushing the valve core 2 to move away from the end wall 114 of the chamber 11. During this process, the elastic element 5 will continue to be compressed, so that the elastic force of the elastic element 5 will continuously increase, and the volume of the pressure chamber 111 formed between the valve core 2 and the end wall 114 of the chamber 11 will also continuously increase, thereby increasing the oil pressure in the pressure chamber 111. When the oil pressure in the pressure chamber 111 increases to not less than the second set value, the valve core 2 moves to the second position where the first liquid flow channel 12 is closed and the second liquid flow channel 13 is open. The oil pressure in the pressure chamber 111 can be balanced with the elastic force of the elastic element 5 again, so that the valve core 2 can be stabilized in the second position.

[0055] It should also be noted that those skilled in the art can calculate the first set value and the second set value based on factors such as the oil resistance characteristics of the lubricating oil at different temperatures, the size of the pressure chamber 111, and the weight of the valve core 2, and select and adjust the first set value and the second set value based on the above factors.

[0056] In some embodiments, such as Figure 1As shown, the second end 22 of the valve core 2 may have a mounting groove 222. A part of the spring extends into the mounting groove 222 and connects with the mounting groove 222, which can ensure that the spring moves along the axial direction of the valve core 2 when it moves, without deflection.

[0057] In some embodiments, the first set value is equal to the spring's deformation pressure threshold, which refers to the spring just undergoing elastic deformation when the axial force it experiences is the first set value.

[0058] In some embodiments, the elastic element 5 can also be replaced by a two-way pressure valve, which includes a first valve body and a second valve body sharing a common valve body. Each of the first and second valve bodies includes a valve core and an elastic structure for applying an elastic preload to the valve core. The first valve core is disposed at a first end of the two-way pressure valve, and the second valve core is disposed at a second end of the two-way pressure valve. The first and second valve cores are capable of telescopic movement along the connection direction between the first and second ends. When the oil pressure in the pressure chamber 111 is less than a first set value, the two-way pressure valve is closed; when the oil pressure is not greater than a second set value, the two-way pressure valve is open, and the first and / or second valve cores are capable of axial movement.

[0059] It should be noted that the elastic element 5 provided in the embodiments of this application can also be replaced with other components that can achieve the same function, except for the spring and the two-way pressure valve. Those skilled in the art can select and adjust according to actual needs.

[0060] In some embodiments, the axial direction of the valve sleeve 1 and the axial direction of the valve core 2 can be parallel to the ground. In this arrangement, the movement direction of the valve core 2 is also parallel to the ground and will not be affected by gravity. The opening and closing of the valve core 2 will also be more precise.

[0061] In one implementation of the embodiments of this application, such as Figure 1 and Figure 4As shown, two first annular grooves 112 can be formed on the inner wall of the chamber 11. The two first annular grooves 112 are arranged at intervals along the axial direction of the valve sleeve 1. Each first annular groove 112 is provided with a first annular protrusion 1121 to divide the first annular groove 112 into a first sub-groove 1122 and a second sub-groove 1123. The two first sub-grooves 1122 are respectively connected to the oil tank 3. Among the two second sub-grooves 1123, the second sub-groove 1123 closer to the pressure chamber 111 is connected to the inlet end of the oil cooler 4, and the second sub-groove 1123 further away from the pressure chamber 111 is connected to the inlet end of the oil cooler 4. The second sub-groove 1123 of cavity 111 is connected to the outlet end of oil cooler 4; two second annular grooves 23 can be opened on the outer side wall of valve core 2. The two second annular grooves 23 are arranged at intervals along the axial direction of valve core 2. Among the two first annular protrusions 1121, when one of the first annular protrusions 1121 near pressure cavity 111 faces the second annular groove 23 near pressure cavity 111, the first liquid flow channel 12 is opened; when the other first annular protrusion 1121 faces the second annular groove 23 away from pressure cavity 111, the second liquid flow channel 13 is opened.

[0062] In other words, the two first annular grooves 112 formed on the inner wall of the chamber 11 can be referred to as the first oil groove and the second oil groove, respectively. The first oil groove is closer to the end wall 114 of the chamber 11 (closer to the pressure chamber 111), and the second oil groove is located on the side of the first oil groove away from the end wall 114 (closer to the elastic member 5). The first oil groove has a first annular protrusion 1121, which divides the first oil groove into a first sub-groove 1122 and a second sub-groove 1123, which can be referred to as the first inlet oil groove and the first outlet oil groove, respectively. The first inlet oil groove is closer to the end wall 114 of the chamber 11, and the first outlet oil groove is located on the side of the first inlet oil groove away from the end wall 114 (closer to the elastic member 5). The first inlet oil groove is connected to the oil tank 3, and the first outlet oil groove is connected to the inlet end of the oil cooler 4. The first oil groove can function as the first liquid flow channel 12 connecting the oil cooler 4.

[0063] Similarly, the second oil tank has a first annular protrusion 1121, which divides the second oil tank into a first sub-groove 1122 and a second sub-groove 1123, which can be referred to as the second inlet oil tank and the second outlet oil tank, respectively. The second inlet oil tank is located near the end wall 114 of the chamber 11 (near the pressure chamber 111), and the second outlet oil tank is located on the side of the second inlet oil tank away from the end wall 114 (near the elastic member 5). The second inlet oil tank is connected to the oil tank 3, and the second outlet oil tank is connected to the outlet end of the oil cooler 4. This second oil tank can function as a second liquid flow channel 13 that avoids the oil cooler 4.

[0064] The two second annular grooves 23 opened on the outer side wall of the valve core 2 can be referred to as the first connecting groove and the second connecting groove, respectively. The first connecting groove is close to the end wall 114 of the chamber 11 (close to the pressure chamber 111), and the second connecting groove is located on the side of the first connecting groove away from the end wall 114 (close to the elastic element 5).

[0065] In one example, when the oil temperature is high, the lubricating oil has good fluidity, such as... Figure 2 As shown, at this time, the oil pressure cannot overcome the elastic force of the spring to push the valve core 2 to move. The first annular groove 112 and the second annular groove 23 on the side near the end wall 114 are opposite each other, forming the first liquid flow channel 12 mentioned above. The lubricating oil in the oil tank 3 can flow to the oil cooler 4 through the first liquid flow channel 12. And the first annular protrusion 1121 on the side away from the end wall 114 abuts against the valve core 2, so that the first sub-groove 1122 and the second sub-groove 1123 are not connected to each other, thereby closing the second liquid flow channel 13. The higher temperature oil will not bypass the oil cooler 4 and be delivered to the lubricated parts to be cooled. For example, when the oil pressure in the pressure chamber 111 is lower than the first set value, and the valve core 2 is in the first position, such as Figure 2 As shown, the first annular protrusion 1121 in the first oil tank faces the first connecting groove, so that the first connecting groove can connect the first inlet oil tank and the first outlet oil tank separated by the first annular protrusion 1121. The lubricating oil supplied by the oil tank 3 to the first inlet oil tank can flow through the first connecting groove to the first outlet oil tank, and then to the oil cooler 4, that is, the first liquid flow channel 12 is opened. At this time, the first annular protrusion 1121 in the second oil tank abuts against the valve core 2, and the second inlet oil tank and the second outlet oil tank are blocked by the valve core 2 and cannot be connected, and the second liquid flow channel 13 is closed.

[0066] In another example, lubrication is less fluid when the oil temperature is low. For example... Figure 3 As shown, at this time, the oil pressure can overcome the elastic force of the spring and push the valve core 2 to move. The first annular groove 112 on the side away from the end wall 114 is opposite to the second annular groove 23, forming the aforementioned second liquid flow channel 13 inside. The lubricating oil at a lower temperature can flow through the second liquid flow channel 13, bypassing the oil cooler 4, to the component to be cooled and lubricated. For example, when the oil pressure in the pressure chamber 111 is not lower than the second set value, when the valve core 2 moves to the second position, as... Figure 3As shown, the first annular protrusion 1121 in the second oil tank faces the second connecting groove, so that the second connecting groove can connect the second inlet oil tank and the second outlet oil tank separated by the first annular protrusion 1121. The lubricating oil supplied by the oil tank 3 to the second inlet oil tank can flow to the second outlet oil tank through the second connecting groove, and then bypass the oil cooler 4 to be directly supplied to the component to be cooled, that is, the second liquid flow channel 13 is opened; at this time, the first annular protrusion 1121 in the first oil tank abuts against the valve core 2, the first inlet oil tank and the first outlet oil tank are blocked by the valve core 2 and cannot be connected, and the first liquid flow channel 12 is closed.

[0067] In some embodiments, such as Figure 4 As shown, the length of the second annular groove 23 can be less than the length of the first annular groove 112. When the oil pressure is not less than the second set value, the valve core 2 can move a smaller distance to close the first liquid flow channel 12 and open the second liquid flow channel 13, which is more convenient for fine control.

[0068] As described in the above embodiments, when the oil pressure in the pressure chamber 111 is greater than or equal to the first set value, the valve core 2 moves away from the end wall 114 to open the second liquid flow channel 13 and close the first liquid flow channel 12. To achieve the most ideal effect, the first liquid flow channel 12 needs to be exactly closed when the second liquid flow channel 13 is open. This places stringent requirements on the accuracy of the valve core 2's movement distance. Furthermore, the temperature, flow rate, and flow volume of the lubricating oil are not constant during actual circulation, making it difficult to fully achieve the ideal requirement.

[0069] Therefore, in one implementation of the embodiments of this application, such as Figure 4 As shown, in the two second annular grooves 23, the second annular groove 23 away from the pressure chamber 111 has a second annular protrusion 231, and the side of the second annular protrusion 231 facing the inner wall of the chamber 11 has a first inclined surface 2311. The first inclined surface 2311 is inclined so that the side away from the pressure chamber 111 is further away from the central axis of the valve core 2.

[0070] In other words, a second annular protrusion 231 can be provided in the second connecting groove opened on the outer side wall of the valve core 2 to divide the second connecting groove into a first sub-connecting groove and a second sub-connecting groove, wherein the first sub-connecting groove is opposite to the second inlet oil groove, and the second sub-connecting groove is opposite to the second outlet oil groove. Figure 2 As shown, when the first annular protrusion 1121 in the second oil tank contacts the second annular protrusion 231, the second inlet oil tank and the second outlet oil tank are not connected, thereby closing the second liquid flow channel 13; Figure 3As shown, when the first annular protrusion 1121 in the second oil tank is partially or completely offset from the second annular protrusion 231, so that the first annular protrusion 1121 is opposite to the first sub-connecting groove, the first sub-connecting groove can connect the second inlet oil tank and the second outlet oil tank, thereby closing the second liquid flow channel 13.

[0071] A first inclined surface 2311 is provided on the second annular protrusion 231. When the valve core 2 moves away from the end wall 114, a gap is formed between the first inclined surface 2311 and the first annular protrusion 1121 when the first liquid flow channel 12 is not completely closed, allowing a portion of the liquid to flow through from the second inlet oil tank to the second outlet oil tank. As the valve core 2 continues to move, the gap gradually increases until the first liquid flow channel 12 is completely closed and the second liquid flow channel 13 is completely open. In this configuration, the accuracy requirement for the movement distance of the valve core 2 is not high.

[0072] In addition, in the above embodiment without the first inclined surface 2311, as the valve core 2 gradually begins to move until the first liquid flow channel 12 is closed, only a very small portion of the lubricating oil can pass through the first liquid flow channel 12 at this time, while the remaining lubricating oil accumulates in the oil circuit and in the closed second liquid flow channel 13. At this time, the oil pressure is relatively high. If the first liquid flow channel 12 is closed and the second liquid flow channel 13 is opened at this time, a large impact force will be generated, which may cause damage to the valve core 2 and the valve sleeve 1.

[0073] In the cooling and lubrication system provided in this application embodiment, a first inclined surface 2311 is provided on the second annular protrusion 231, so that there is a buffer process between the closing of the first liquid flow channel 12 and the opening of the second liquid flow channel 13. This not only reduces the accuracy requirements of the valve core 2 movement distance, but also avoids damage to the valve core 2 and other components by impact force.

[0074] In some embodiments of this application, such as Figure 1 As shown, the end face of the first end 21 can protrude partially toward the second end 22 away from the valve core 2 to form a boss 211. The side of the boss 211 away from the second end 22 is configured to abut against the end wall 114 of the chamber 11 to form a pressure chamber 111 between the boss 211 and the inner wall of the chamber 11. The first end 21 is opposite to the second end 22.

[0075] In the cooling and lubrication system provided in this application embodiment, the stability of the valve core 2 in maintaining a first position is improved by providing a boss 211 on the valve core 2 that is suitable for abutting against the end wall 114 of the chamber 11. In this case, the elastic member 5 can be in a pre-compressed state, so that the boss 211 can abut against the end wall 114. And since the end face of the first end 21 of the valve core 2 only partially protrudes to form a boss, there will be a certain gap between the non-protruding part of the end face and the end wall 114, which can serve as a pressure chamber 111. Lubricating oil can enter and fill this gap to fill the space between the end face of the first end 21 and the end wall 114, and generate a thrust along the axial direction of the valve core 2. When the oil pressure is large enough, it can overcome the elastic force of the elastic member 5 and move.

[0076] In some embodiments, in order to facilitate oil actuation, the valve sleeve 1 can be provided with an oil inlet on the side away from the fixed plate 6. The extension direction of the oil inlet is parallel to the axial direction of the valve core 2. Lubricating oil can enter the pressure chamber 111 through the oil inlet, and the flow direction of the lubricating oil is parallel to the axial direction of the valve core 2. It can directly generate axial impact force and pressure on the valve core 2, and can push the valve core 2 more easily.

[0077] However, this configuration increases the axial space required for the cooling and lubrication system, thus increasing the space occupied by the hybrid transmission. To save space on the hybrid transmission, such as... Figure 1 As shown, the axial direction of the oil inlet can be perpendicular to the axial direction of the valve core 2. When the lubricating oil fills the pressure chamber 111, the above-mentioned technical effect can still be achieved.

[0078] However, with this type of oil inlet, the flow direction of lubricating oil is perpendicular to the axis of valve core 2. A portion of the oil will impact valve core 2 in a direction perpendicular to the side wall of boss 211. The direction of the impact force is perpendicular to the movement direction of valve core 2, which may cause damage to valve core 2.

[0079] Therefore, in some embodiments of this application, such as Figure 1 As shown, the sidewall of the boss 211 includes a second inclined surface 2111, which is inclined such that the closer it is to the end wall 114 of the chamber 11, the closer it is to the central axis of the valve core 2.

[0080] When lubricating oil flows into pressure chamber 111 from the oil inlet, some of the lubricating oil will flow onto the second inclined surface 2111, thereby generating a component force along the axial direction of valve core 2, which can more easily push valve core 2 to move.

[0081] Furthermore, when the lubricating oil flows to the second inclined surface 2111, the second inclined surface 2111 has a certain guiding effect, which can disperse part of the impact force perpendicular to the axial direction, thereby avoiding damage to the valve core 2 and extending the service life of the valve core 2.

[0082] In addition, in one implementation of the embodiments of this application, such as Figure 1 As shown, a third annular groove 113 is provided on the inner side wall of the chamber 11, and the third annular groove 113 is close to the end wall 114 of the chamber 11; when the boss 211 abuts against the end wall 114 of the chamber 11, the boss 211 is at least partially located in the third annular groove 113.

[0083] In the cooling and lubrication system provided in this application embodiment, by providing the third annular groove 113, the volume of the pressure chamber 111 can be increased, that is, the volume of lubricating fluid that the pressure chamber 111 can store is increased, the maximum oil pressure in the pressure chamber 111 is increased, and the valve core 2 can be moved more easily.

[0084] During the circulation of lubricating oil, the oil cooler 4 may become clogged. In this case, regardless of the temperature of the lubricating oil, it can still push the valve core 2 to move and flow through the second liquid flow channel 13 to the components to be cooled and lubricated. Although the high-temperature lubricating oil flows to the components to be cooled and lubricated, reducing the working efficiency of the hybrid transmission, it will not cause damage to other components due to the damage to the oil cooler 4.

[0085] However, the oil cooler 4 is blocked, and the lubricating oil cannot be effectively cooled during circulation, remaining at a high temperature. At this time, the lubricating oil has good fluidity, meaning that the flow rate of the lubricating oil entering the system is relatively large. However, the flow rate that the second liquid flow channel 13 can withstand is limited. Under pressure, the remaining lubricating oil can only return to the oil tank 3, creating a countercurrent with the lubricating oil flowing out of the oil tank 3, which in turn causes damage to components such as pipelines, oil tank 3, and valve core 2.

[0086] Therefore, in some embodiments of this application, such as Figure 5 As shown, the cooling and lubrication system may further include: an oil supply line 7, an oil supply pump 8, and an overflow valve 9; the oil supply line 7 includes a main oil line 71, three branch oil lines 72, and a first bypass oil line 73, wherein one end of the main oil line 71 is connected to the oil tank 3, and the other end is connected to the three branch oil lines 72 respectively, and the oil supply pump 8 is installed on the main oil line 71; the three branch oil lines 72 are respectively connected to the first liquid flow channel 12, the second liquid flow channel 13, and the pressure chamber 111; one end of the first bypass oil line 73 is connected to the inlet end of the oil supply pump 8, and the other end is connected between the outlet end of the oil supply pump 8 and the three branch oil lines 72, and the overflow valve 9 is installed on the first bypass oil line 73, and the inlet end of the overflow valve 9 is connected to the outlet end of the oil supply pump 8.

[0087] A first bypass oil passage 73 is provided on the main oil passage 71. When the oil cooler 4 is blocked and the flow rate of lubricating oil is large, the overflow valve 9 opens. Figure 6As shown, a portion of the lubricating oil enters the second liquid flow channel 13 along the main oil passage 71 and the branch oil passage 72, and is finally delivered to the parts to be cooled and lubricated; another portion of the lubricating oil enters the first bypass oil passage 73 from the main oil passage 71, circles around the first bypass oil passage 73 and returns to the oil tank 3 or back to the main oil passage 71, and is delivered to the parts to be cooled and lubricated, thus achieving the overflow protection function.

[0088] In one implementation of the embodiments of this application, such as Figure 5 As shown, the cooling and lubrication system may also include a first check valve 10, which is disposed on the main oil circuit 71, and the inlet end of the first check valve 10 is connected to the outlet end of the oil supply pump 8.

[0089] To further ensure that the lubricating oil entering the first liquid flow channel 12 and / or the second liquid flow channel 13 does not return to the oil tank 3 along the main oil passage 71, a first check valve 10 is provided on the main oil passage 71 to restrict the flow direction of the lubricating oil on the main oil passage 71.

[0090] In one implementation of the embodiments of this application, such as Figure 5 As shown, the oil supply line 7 also includes a second bypass oil line 74, and the cooling and lubrication system also includes another check valve (hereinafter referred to as the second check valve 101); one end of the second bypass oil line 74 is connected to the inlet end of the oil supply pump 8, and the other end is connected between the outlet end of the oil supply pump 8 and the three branch oil lines 72. The second check valve 101 is disposed on the second bypass oil line 74, and the inlet end of the second check valve 101 is connected to the inlet end of the oil supply pump 8.

[0091] When a car decelerates or brakes, the hybrid vehicle's electric motor can reverse its rotation to convert kinetic energy into electrical energy, thus recovering energy. In this situation, the motor reverses and drives the fuel pump 8 in the hybrid transmission to reverse as well, helping to reduce the vehicle's speed and store kinetic energy in the battery for later use.

[0092] As can be seen from the above embodiments, a first check valve 10 is provided on the main oil circuit 71 and an overflow valve 9 is provided on the first bypass oil circuit 73. When the motor reverses and drags the oil supply pump 8 to reverse, it cannot draw lubricating oil from the above two oil circuits, and it is easy to cause a vacuum.

[0093] In the cooling and lubrication system provided in this application embodiment, a second bypass oil passage 74 is provided on the main oil passage 71. When the oil supply pump 8 reverses, a portion of the oil enters the second bypass oil passage 74 from the oil tank 3 and then enters the oil supply pump 8 from the main oil passage 71, so that there will be no cavitation.

[0094] Furthermore, a second check valve 101 is provided on the second bypass oil passage 74, which can restrict the flow direction of lubricating oil on the second bypass oil passage 74.

[0095] This application also provides a hybrid transmission including the aforementioned cooling and lubrication system.

[0096] In the hybrid transmission provided in this application embodiment, the valve core 2 is located inside the valve sleeve 1 and can move along the extending direction of the chamber 11 inside the valve sleeve 1. When the temperature of the lubricating oil rises or falls, the oil pressure inside the pressure chamber 111 also changes accordingly, pushing the valve core 2 to move, thereby opening the first liquid flow channel 12 or the second liquid flow channel 13. This allows lubricating oil of different temperatures to selectively flow through the oil cooler 4 and cool and lubricate the components to be cooled. Compared with the cooling and lubrication systems in related technologies, the cooling and lubrication system provided in this application takes into account the oil resistance characteristics of lubricating oil at different temperatures. This allows lubricating oil at higher temperatures to flow through the oil cooler 4 for cooling, while lubricating oil at lower temperatures can bypass the oil cooler 4 and flow to the components to be cooled. The hybrid transmission can always operate in a high-efficiency range, improving the working efficiency of the hybrid transmission.

[0097] 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.

[0098] Other embodiments of this application will readily occur to those skilled in the art upon consideration of the specification and practice of the invention 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.

[0099] 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.

Claims

1. A cooling and lubrication system, characterized in that, The cooling and lubrication system includes: valve sleeve (1), valve core (2), oil tank (3) and oil cooler (4); The valve sleeve (1) has a chamber (11), a first liquid flow channel (12) and a second liquid flow channel (13) inside. The oil tank (3) is connected to the inlet end of the oil cooler (4) through the first liquid flow channel (12) and the oil tank (3) is connected to the outlet end of the oil cooler (4) through the second liquid flow channel (13). The valve core (2) is located at least partially within the chamber (11) and is movably connected to the valve sleeve (1). There is a gap between the first end (21) of the valve core (2) and the end wall (114) of the chamber (11) to form a pressure chamber (111), which is connected to the oil tank (3). When the oil pressure in the pressure chamber (111) is lower than a first set value, the valve core (2) is in a first position, so that the first liquid flow channel (12) is opened and the second liquid flow channel (13) is closed; when the oil pressure in the pressure chamber (111) is not lower than a second set value, the valve core (2) moves to a second position away from the end wall (114) of the chamber (11), so that the first liquid flow channel (12) is closed and the second liquid flow channel (13) is opened, wherein the oil pressure in the pressure chamber (111) is related to the temperature of the lubricating oil in the oil tank (3).

2. The cooling and lubrication system according to claim 1, characterized in that, The cooling and lubrication system also includes an elastic element (5) and a fixing plate (6); One end of the elastic element (5) is connected to the fixed plate (6), and the other end is connected to the second end (22) of the valve core (2), and is used to drive the valve core (2) to move toward the end wall (114) of the chamber (11), with the first end (21) and the second end (22) opposite to each other.

3. The cooling and lubrication system according to claim 1, characterized in that, Two first annular grooves (112) are provided on the inner wall of the chamber. The two first annular grooves (112) are arranged at intervals along the axial direction of the valve sleeve (1). Each first annular groove (112) is provided with a first annular protrusion (1121) to divide the first annular groove (112) into a first sub-groove (1122) and a second sub-groove (1123). The two first sub-grooves (1122) are respectively connected to the oil tank (3). Among the two second sub-grooves (1123), the second sub-groove (1123) closer to the pressure chamber (111) is connected to the inlet end of the oil cooler (4), and the second sub-groove (1123) farther away from the pressure chamber (111) is connected to the outlet end of the oil cooler (4). Two second annular grooves (23) are provided on the outer side wall of the valve core (2). The two second annular grooves (23) are arranged at intervals along the axial direction of the valve core (2). Among the two first annular protrusions (1121), when one of the first annular protrusions (1121) near the pressure chamber (111) faces the second annular groove (23) near the pressure chamber (111), the first liquid flow channel (12) is opened; when the other first annular protrusion (1121) faces the second annular groove (23) away from the pressure chamber (111), the second liquid flow channel (13) is opened.

4. The cooling and lubrication system according to claim 3, characterized in that, In one of the two second annular grooves (23), away from the pressure chamber (111), there is a second annular protrusion (231), and the second annular protrusion (231) has a first inclined surface (2311) on the side facing the inner wall of the chamber (11), and the first inclined surface (2311) is inclined so that it is further away from the pressure chamber (111) and further away from the central axis of the valve core (2).

5. The cooling and lubrication system according to claim 1, characterized in that, The end face of the first end (21) protrudes partially toward the second end (22) away from the valve core (2) to form a boss (211). The side of the boss (211) away from the second end (22) is configured to abut against the end wall (114) of the chamber (11) to form the pressure chamber (111) between the boss (211) and the inner wall of the chamber (11). The first end (21) is opposite to the second end (22).

6. The cooling and lubrication system according to claim 5, characterized in that, The sidewall of the boss (211) includes a second inclined surface (2111), which is inclined such that the closer the end wall (114) is to the chamber (11), the closer it is to the central axis of the valve core (2).

7. The cooling and lubrication system according to claim 5, characterized in that, A third annular groove (113) is provided on the inner wall of the chamber (11), and the third annular groove (113) is close to the end wall of the chamber (11); When the boss (211) abuts against the end wall (114) of the chamber (11), the boss (211) is at least partially located within the third annular groove (113).

8. The cooling and lubrication system according to claim 1, characterized in that, The cooling and lubrication system also includes: an oil supply line (7), an oil supply pump (8), and an overflow valve (9); The oil supply pipeline (7) includes a main oil line (71), three branch oil lines (72) and a first bypass oil line (73). One end of the main oil line (71) is connected to the oil tank (3), and the other end is connected to the three branch oil lines (72) respectively. The oil supply pump (8) is installed on the main oil line (71). The three branch oil lines (72) are connected to the first liquid flow channel (12), the second liquid flow channel (13) and the pressure chamber (111) respectively. One end of the first bypass oil line (73) is connected to the inlet end of the oil supply pump (8), and the other end is connected between the outlet end of the oil supply pump (8) and the three branch oil lines (72). The overflow valve (9) is installed on the first bypass oil line (73), and the inlet end of the overflow valve (9) is connected to the outlet end of the oil supply pump (8).

9. The cooling and lubrication system according to claim 8, characterized in that, The oil supply line (7) also includes a second bypass oil line (74), and the cooling and lubrication system also includes a check valve; One end of the second bypass oil passage (74) is connected to the inlet end of the oil supply pump (8), and the other end is connected between the outlet end of the oil supply pump (8) and the three branch oil passages (72). The one-way valve is installed on the second bypass oil passage (74), and the inlet end of the one-way valve is connected to the inlet end of the oil supply pump (8).

10. A hybrid transmission, characterized in that, Includes the cooling and lubrication system as described in any one of claims 1 to 9.

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