Fluid pressure control system of hybrid transmission

Abstract

To provide a fluid pressure control system of a hybrid transmission.SOLUTION: A fluid pressure control system includes a cooling lubrication oil passage, a drive oil passage, an oil supply passage, a pressure control valve, a three position electromagnetic valve and a switching / accumulating integrated valve, wherein the oil supply passage communicates with each of a liquid inlet of the pressure control valve, a front control port of the pressure control valve, a liquid inlet of the three position electromagnetic valve and a liquid inlet of the switching / accumulating integrated valve, and supplies hydraulic oil, a second liquid outlet of the three position electromagnetic valve communicates with a rear control port of the pressure control valve, a third liquid outlet of the three position electromagnetic valve communicates with a driving port of the switching / accumulating integrated valve, the cooling lubrication oil passage communicates with a liquid outlet of the pressure control valve, and supplies hydraulic oil to a hybrid system, the drive oil passage communicates with a liquid outlet of the switching / accumulating integrated valve, and supplies high pressure oil to a clutch, and the three position electromagnetic valve can control a hydraulic state of hydraulic oil in the oil supply passage and an opening / closing state of the three position electromagnetic valve.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to the technical field of transmissions, and more particularly to a hydraulic control system for a hybrid transmission. [Background technology]

[0002] With the development of new energy vehicle technology, hybrid vehicles can achieve good overall vehicle economy by improving engine operating efficiency and recovering braking energy, provided that the overall vehicle power requirements are met. Therefore, against the background of broad market demand, strict fuel economy restrictions, and higher overall vehicle performance requirements, developing a highly efficient hybrid system is an effective way to solve the above problems.

[0003] A hydraulic control system is an important component of a hybrid system that supplies high-pressure hydraulic oil (engine oil) to the clutch to achieve hydraulic control of the clutch, and also supplies hydraulic oil to components in the hybrid system that need to be cooled and lubricated to cool and lubricate them. A hydraulic control system typically includes a pressure regulator valve and a switching valve. The pressure regulator valve adjusts the hydraulic pressure of the system, and the switching valve controls the connection and disconnection of the oil passages and further controls the state of the clutch. Therefore, conventional hydraulic control systems require multiple solenoid valves to drive and operate the pressure regulator valve and the switching valve, respectively. As a result, hydraulic control systems require a large number of parts, a complex structure, a large space, and high manufacturing costs. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Chinese Patent No. 115574089 Summary of the Invention [Problem to be solved by the invention]

[0005] The present invention discloses a hydraulic control system for a hybrid transmission that overcomes or at least partially solves the above problems. [Means for solving the problem]

[0006] In order to achieve the above object, the present invention employs the following technical aspects.

[0007] The present invention discloses a hydraulic control system for a hybrid transmission, the hydraulic control system including a cooling and lubricating oil passage, a driving oil passage, an oil supply oil passage, a pressure regulating valve, a three-position solenoid valve, and a switching and energy storage integrated valve, the oil supply passage communicates with the inlet of the pressure regulating valve, the front control port of the pressure regulating valve, the inlet of the three-position solenoid valve, and the inlet of the integrated switching and energy storage valve, respectively, and is for supplying hydraulic oil; a second outlet of the three-position solenoid valve communicates with the rear control port of the pressure regulating valve, and a third outlet of the three-position solenoid valve communicates with the drive port of the integrated switching and energy storage valve; the cooling and lubricating oil passage communicates with the outlet of the pressure regulating valve and is for feeding hydraulic oil to a hybrid system; and the drive oil passage communicates with the outlet of the integrated switching and energy storage valve and is for supplying high-pressure oil to a clutch, When the inlet of the three-position solenoid valve is not in communication with either the second outlet of the three-position solenoid valve or the third outlet of the three-position solenoid valve, the hydraulic oil in the oil supply line is in a low-pressure state and the integrated switching and energy storage valve is closed, when the inlet of the three-position solenoid valve is in communication only with the second outlet of the three-position solenoid valve, the hydraulic oil in the oil supply line is in a high-pressure state and the integrated switching and energy storage valve is closed, and when the inlet of the three-position solenoid valve is in communication with both the second outlet of the three-position solenoid valve and the third outlet of the three-position solenoid valve, the hydraulic oil in the oil supply line is in a high-pressure state and the integrated switching and energy storage valve is opened.

[0008] Furthermore, the integrated switching and energy storage valve includes a first valve body, a first valve spool, a first elastic member, and an energy storage elastic member, a first valve cavity is provided within the first valve body, and a drive port communicating with the first valve cavity is provided at a rear end of the first valve body; the first valve body is provided with a first liquid inlet and a first liquid outlet, each communicating with the first valve cavity, and an energy storage flow path communicating with the first liquid outlet; the first valve spool is located in the first valve cavity and is piston-movable along the front-rear direction of the first valve cavity; an energy storage cavity communicating with the energy storage passage is formed between a front portion of the first valve spool and an inner cavity wall of the first valve cavity; and the energy storage cavity expands along the moving direction of the first valve spool when the first valve spool moves forward; the first elastic member is for holding the first valve spool in a blocking position where communication between the first liquid inlet and the first liquid outlet is blocked, and when pressurized driving fluid enters through the driving port, the first valve spool is driven to overcome the elastic force of the first elastic member and move forward to an open position where communication between the first liquid inlet and the first liquid outlet is established, The energy-storing elastic member is provided in the first valve cavity on the front side of the energy-storing cavity, and serves to supply an elastic force to the first valve spool that suppresses expansion of the energy-storing cavity.

[0009] Furthermore, a connecting groove or a connecting hole is formed in the first valve spool, and when the first valve spool is in the open position, the connecting groove or the connecting hole connects the first liquid inlet and the first liquid outlet.

[0010] Furthermore, a first relief hole is formed at the front end of the first valve body, and the first relief hole communicates with the energy storage cavity through a gap between the first valve spool and the first valve body.

[0011] Furthermore, the integrated switching and energy storage valve further includes a fixing bolt, The fixing bolt is inserted into the first valve cavity from the front end of the first valve body and fixed therein; a first accommodating cavity is formed in the front portion of the first valve spool; a second accommodating cavity communicating with the first accommodating cavity is formed in the middle portion of the first valve spool; the front end of the fixing bolt is inserted from the first accommodating cavity into the second accommodating cavity; the first elastic member is located in the second accommodating cavity; one end of the first elastic member abuts against the front end of the fixing bolt; the other end of the first elastic member abuts against the first valve spool; the energy-storing elastic member is located in the first accommodating cavity; one end of the energy-storing elastic member is fixedly connected to the fixing bolt; and the first relief hole is opened in the fixing bolt.

[0012] The three-position solenoid valve further includes a second valve body, a second valve spool, a second elastic member, and an electromagnetic part, a second valve cavity is provided within the second valve body, a second liquid inlet is provided at a front end of the second valve cavity, and a second liquid outlet and a third liquid outlet are provided in the second valve body in this order from front to rear, the second liquid outlet and the second valve cavity being respectively connected to the second valve cavity; the second valve spool is located in the second valve cavity and is piston-movable along the front-rear direction of the second valve cavity; the second elastic member is for holding the second valve spool in a first position at which communication between the second liquid inlet and the second and third liquid outlets is blocked, The electromagnetic unit is provided at the rear end of the second valve body and supplies two types of electromagnetic forces of different magnitudes to drive the second valve spool to move to a second position where the second liquid inlet is connected only to the second liquid outlet by overcoming the elastic force of the second elastic member, or to a third position where the second liquid inlet is connected to both the second liquid outlet and the third liquid outlet.

[0013] Furthermore, a second relief hole is formed in the second valve spool, and the rear end of the second relief hole extends from the rear end of the second valve body to the outside of the second valve cavity, and when the second valve spool is located in the first position, the front end of the second relief hole is connected to the second outlet port.

[0014] Further, the apparatus further includes a mechanical oil pump, a filter, and a circulation oil passage; An oil outlet end of the mechanical oil pump communicates with the oil supply line, an oil inlet end of the mechanical oil pump communicates with an oil tank via the filter, one end of the circulation oil line communicates with the oil supply line, and the other end of the circulation oil line communicates with the oil inlet end of the mechanical oil pump, and a first check valve is provided in the circulation oil line, and hydraulic oil in the circulation oil line can only flow to the oil supply line via the first check valve.

[0015] further including an electric oil pump and a second check valve; The oil inlet end of the electric oil pump is connected to the oil tank via the filter, and the oil outlet end of the electric oil pump is connected to the cooling lubrication oil passage via the second check valve, so that the hydraulic oil at the oil outlet end of the electric oil pump can only flow to the cooling lubrication oil passage via the second check valve.

[0016] Further, the system further includes a relief valve and a cooler; The relief valve has an inlet and a control port both connected to the cooling lubricant oil passage, and an outlet connected to an oil tank. When the oil pressure in the cooling lubricant oil passage is greater than a predetermined value, the cooling lubricant oil passage is connected to the oil tank. When the oil pressure in the cooling lubricant oil passage is not greater than the predetermined value, the cooling lubricant oil passage is disconnected from the oil tank. The cooler is provided in the cooling lubrication oil passage and is intended to cool the hydraulic oil in the cooling lubrication oil passage. The oil outlet end of the cooling lubrication oil passage is divided into a plurality of oil discharge branch passages, and a throttling member is provided in each of the oil discharge branch passages. [Effects of the Invention]

[0017] The advantages and beneficial effects of the present invention are as follows:

[0018] In the hydraulic control system of the present invention, a single three-position solenoid valve can be used to control the operation of the pressure regulating valve and the integrated switching / energy storage valve, and can also control the hydraulic pressure state of the hydraulic oil in the oil supply line and the supply of high-pressure oil to the clutch, resulting in advantages such as a simple structure, a small number of parts used, low manufacturing costs, and a small space occupation. [Brief explanation of the drawings]

[0019] Various other benefits and advantages will become apparent to those skilled in the art upon reading the following detailed description of the preferred embodiments. The drawings are only for purposes of illustrating the preferred embodiments and are not to be construed as limiting the invention. Furthermore, like reference numerals are used throughout the drawings to refer to like parts.

[0020] [Figure 1] FIG. 1 is a structural schematic diagram of a hydraulic control system for a hybrid transmission according to one embodiment of the present invention. [Figure 2] FIG. 2 is an axial cross-sectional view of an integrated switching and energy storage valve in one embodiment of the present invention when closed. [Figure 3] FIG. 3 is an axial cross-sectional view of an integrated switching and energy storage valve in an embodiment of the present invention when opened. [Figure 4] FIG. 4 is an axial cross-sectional view of an integrated switching / energizing valve in an embodiment of the present invention when energized. [Figure 5] FIG. 5 is an axial cross-sectional view of a three-position solenoid valve according to an embodiment of the present invention when the second valve spool is in the first position. [Figure 6] FIG. 6 is an axial cross-sectional view of a three-position solenoid valve according to an embodiment of the present invention when the second valve spool is in the second position. [Figure 7] FIG. 7 is an axial cross-sectional view of a three-position solenoid valve according to an embodiment of the present invention when the second valve spool is in the third position. DETAILED DESCRIPTION OF THE INVENTION

[0021] In order to make the objectives, technical aspects and advantages of the present invention clearer, the technical aspects of the present invention will be clearly and completely described below in conjunction with specific embodiments of the present invention and corresponding drawings. Obviously, the described embodiments are only some embodiments of the present invention, and are not all embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative labor fall within the protection scope of the present invention.

[0022] For ease of understanding and explanation of the present invention, the left side of each drawing is the front end or front portion of each valve, and the right side of each drawing is the rear end or rear portion of each valve.

[0023] Hereinafter, technical aspects according to each embodiment of the present invention will be described in detail in conjunction with the drawings.

[0024] One embodiment of the present invention provides a hydraulic control system for a hybrid transmission. As shown in FIG. 1, the hydraulic control system includes a cooling and lubricating oil passage 16, a driving oil passage 17, an oil supply oil passage 18, a pressure regulating valve 19, a three-position solenoid valve 21, and a switching and energy storage integrated valve 20.

[0025] The oil supply passage 18 is connected to the inlet of the pressure regulating valve 19, the front control port of the pressure regulating valve 19, the inlet of the three-position solenoid valve 21, and the inlet of the integrated switching and energy storage valve 20, respectively, for supplying hydraulic oil. Specifically, the oil supply passage 18 includes a first oil supply passage 18-1, a second oil supply passage 18-2, a third oil supply passage 18-3, and a fourth oil supply passage 18-4. The first oil supply passage 18-1 is connected to the inlet of the pressure regulating valve 19, the second oil supply passage 18-2 is connected to the front control port of the pressure regulating valve 19, the third oil supply passage 18-3 is connected to the inlet of the three-position solenoid valve 21, and the fourth oil supply passage 18-4 is connected to the inlet of the integrated switching and energy storage valve 20. The second outlet 25 of the three-position solenoid valve 21 communicates with the rear control port of the pressure regulating valve 19 via the first connecting oil passage 41, the third outlet 26 of the three-position solenoid valve 21 communicates with the drive port 3 of the integrated switching / energy storing valve 20 via the second connecting oil passage 42, the cooling / lubricating oil passage 16 communicates with the outlet of the pressure regulating valve 19 and supplies hydraulic oil to the hybrid system to cool and lubricate the parts in the hybrid system that need to be cooled and lubricated, and the drive oil passage 17 communicates with the outlet of the integrated switching / energy storing valve 20 and supplies high-pressure oil to the clutch 47 to drive and operate (engage) the clutch 47 so that the wheels 49 are driven by the engine.

[0026] Of these, clutch 47 is provided between the engine and wheels 49, and clutch 47 controls whether the engine drives wheels 49 to rotate. Clutch 47 is also provided with sensor 48 for detecting the state of clutch 47, and sensor 48 may be a pressure sensor. Second oil supply passage 18-2 is provided with first throttling member 50, and the number of first throttling members 50 may be one or more. First connecting oil passage 41 is provided with second throttling member 51, and the number of second throttling members 51 may be one or more. Fourth oil supply passage 18-4 is provided with third throttling member 52, and each throttling member is for controlling the flow rate of hydraulic oil in the oil passage in which it is located.

[0027] When the inlet of the three-position solenoid valve 21 is not in communication with either the second outlet 25 of the three-position solenoid valve 21 or the third outlet 26 of the three-position solenoid valve 21, the hydraulic oil in the oil supply passage 18 cannot reach the rear control port of the pressure regulating valve 19 or the drive port 3 of the integrated switching and energy storage valve 20 via the three-position solenoid valve 21, and at this time, the pressure at the front control port of the pressure regulating valve 19 is balanced with the spring force of the pressure regulating valve 19, the hydraulic oil in the oil supply passage 18 is in a low-pressure state, and the integrated switching and energy storage valve 20 is closed. When the inlet of the three-position solenoid valve 21 is in communication only with the second outlet 25 of the three-position solenoid valve 21, the hydraulic oil in the oil supply passage 18 can reach the rear control port of the pressure regulating valve 19 via the three-position solenoid valve 21, and at this time, the pressure at the front control port of the pressure regulating valve 19 is balanced with the spring force of the pressure regulating valve 19, the hydraulic oil in the oil supply passage 18 is in a low-pressure state, and the integrated switching and energy storage valve 20 is closed. When the pressure at the port is balanced between the spring force of pressure regulating valve 19 and the pressure at the rear control port of pressure regulating valve 19, the hydraulic oil in oil supply line 18 is in a high-pressure state, but the hydraulic oil in oil supply line 18 cannot reach drive port 3 of integrated switching and energy storage valve 20 via three-position solenoid valve 21, and integrated switching and energy storage valve 20 is closed, and when the inlet of three-position solenoid valve 21 is connected to both second outlet 25 of three-position solenoid valve 21 and third outlet 26 of three-position solenoid valve 21, the hydraulic oil in oil supply line 18 can reach the rear control port of pressure regulating valve 19 and drive port 3 of integrated switching and energy storage valve 20 via three-position solenoid valve 21, and at this time the hydraulic oil in oil supply line 18 is in a high-pressure state, and integrated switching and energy storage valve 20 is opened.

[0028] The hydraulic control system has the advantages of a simple structure, a small number of parts used, low manufacturing costs, and a small space requirement. Furthermore, a single three-position solenoid valve 21 can be used to control the pressure regulating valve 19 and the integrated switching and energy storage valve 20, further simplifying the structural installation of the hydraulic control system.

[0029] In this embodiment, as shown in FIGS. 2 to 4, the integrated switching and energy storage valve 20 includes a first valve body 1, a first valve spool 7, a first elastic member 9, and an energy storage elastic member 10. The first valve body 1 is provided with a first valve cavity 2, and a drive port 3 communicating with the first valve cavity 2 is provided at the rear end of the first valve body 1. The drive port 3 is for connection to a pipeline (oil passage) that can supply pressurized driving fluid (hydraulic oil). The first valve body 1 is provided with a first liquid inlet 4 and a first liquid outlet 5 that communicate with the first valve cavity 2, respectively, and an energy storage flow path 6 that communicates with the first liquid outlet 5. The hydraulic oil can enter the first valve cavity 2 through the first liquid inlet 4 and then flow out through the first liquid outlet 5. The number of first liquid inlets 4 and first liquid outlets 5 may be one or more and can be set according to specific needs. In this embodiment, the number of first liquid inlets 4 and first liquid outlets 5 is two.

[0030] The first valve spool 7 is located in the first valve cavity 2 and is capable of piston-like movement along the front-to-back direction of the first valve cavity 2. A charging cavity 8 communicating with the charging passage 6 is formed between the front part of the first valve spool 7 and the inner cavity wall of the first valve cavity 2. When the first valve spool 7 moves forward in the first valve cavity 2, the charging cavity 8 expands along the moving direction of the first valve spool 7.

[0031] The first elastic member 9 is used to hold the first valve spool 7 in a blocking position that blocks communication between the first liquid inlet 4 and the first liquid outlet 5. When pressurized driving fluid (hydraulic oil) enters through the drive port 3, the driving fluid generates driving pressure at the drive port 3, driving the first valve spool 7 to overcome the elastic force of the first elastic member 9 and move forward to the open position that connects the first liquid inlet 4 and the first liquid outlet 5. At this time, as shown in FIG. 3, the integrated switching / energy storage valve 20 is opened. When there is no pressure in the driving fluid entering through the drive port 3, the elastic force of the first elastic member 9 drives the first valve spool 7 to move backward and return to the blocking position. At this time, the integrated switching / energy storage valve 20 is closed, as shown in FIG. 2. It should be noted that when the first valve spool 7 is in the shut-off position and the open position, the drive port 3 is not connected to either the first liquid inlet 4 or the first liquid outlet 5 due to blocking by the first valve spool 7.

[0032] The energy-storing elastic member 10 is provided in the first valve cavity 2 on the front side of the energy-storing cavity 8, and serves to supply the first valve spool 7 with an elastic force that suppresses the expansion of the energy-storing cavity 8. As shown in FIG. 4 , when the hydraulic pressure at the first outlet 5 is too high, the hydraulic oil enters the energy-storing cavity 8 through the energy-storing flow path 6, driving the first valve spool 7 to move forward and expanding the energy-storing cavity 8. At this time, the energy-storing elastic member 10 is compressed, and the hydraulic pressure becomes potential energy of the energy-storing elastic member 10, causing it to be stored. When the hydraulic pressure at the first outlet 5 decreases, the elastic force of the energy-storing elastic member 10 drives the first valve spool 7 to move backward, compressing the hydraulic oil in the energy-storing cavity 8, thereby increasing the hydraulic pressure at the first outlet 5. In this way, fluctuations in hydraulic pressure are absorbed by the compressive deformation of the energy-storing elastic member 10, and the hydraulic pressure flowing through the integrated switching / energy-storing valve 20 is made more stable.

[0033] In the integrated switching and energy storage valve 20 of this embodiment, the structural design of the first valve body 1 and the arrangement of the first elastic member 9 allow the first valve spool 7 to be switched between a blocking position where the first liquid inlet 4 and the first liquid outlet 5 are not in communication with each other and an open position where the first liquid inlet 4 and the first liquid outlet 5 are in communication with each other, thereby realizing the closing and opening of the valve. In addition, the first valve body 1 is provided with an energy storage flow path 6 that communicates with the first liquid outlet 5, and a flow path 6 that communicates with the front part of the first valve spool 7 and the first valve cavity 2. Between the inner cavity wall and the valve body, there is formed an energy storage cavity 8 which is connected to the energy storage flow path 6. Therefore, when the first valve spool 7 moves forward, the energy storage cavity 8 expands along the direction of movement of the first valve spool 7, compressing the energy storage elastic member 10, absorbing hydraulic pressure fluctuations at the first liquid outlet 5 and ensuring stable hydraulic pressure at the first liquid outlet 5. The switching / energy storage integrated valve 20 has both a switching function and an energy storage function, and is simple and compact in structure.

[0034] 2 to 4, in this embodiment, the first valve spool 7 is provided with a connecting groove 13, and when the first valve spool 7 is in the open position, the first liquid inlet 4 and the first liquid outlet 5 are communicated through the connecting groove 13. Even when the integrated switching / energizing valve 20 is in the energizing state, the first liquid inlet 4 and the first liquid outlet 5 can still communicate through the connecting groove 13. Of course, in other embodiments, the connecting groove 13 may be replaced with a connecting hole.

[0035] 2 to 4, a first relief hole 11 is formed at the front end of the first valve body 1, and the first relief hole 11 communicates with the energy-storing cavity 8 through a gap between the first valve spool 7 and the first valve body 1. In this way, when the integrated switching / energy-storing valve 20 is closed, the first valve spool 7 returns to the shut-off position, and the hydraulic oil pressure in the energy-storing cavity 8 and the first outlet 5 is released through the first relief hole 11, thereby disengaging the clutch 47. The first relief hole 11 may communicate with the oil tank 34 so that the hydraulic oil relieved through the first relief hole 11 flows into the oil tank 34.

[0036] As shown in FIGS. 2 to 4, the integrated switching and energy storage valve 20 further includes a fixing bolt 12. The fixing bolt 12 penetrates and is fixed into the first valve cavity 2 from the front end of the first valve body 1. A first accommodating cavity 14 is formed in the front part of the first valve spool 7. A second accommodating cavity 15 communicating with the first accommodating cavity 14 is formed in the middle part of the first valve spool 7. The front end of the fixing bolt 12 penetrates from the first accommodating cavity 14 into the second accommodating cavity 15. The first elastic member 9 is located in the second accommodating cavity 15. One end of the first elastic member 9 abuts against the rear end of the fixing bolt 12. The other end of the first elastic member 9 abuts against the first valve spool 7. The energy-storing elastic member 10 is located in the first accommodating cavity 14, i.e., between the fixing bolt 12 and the first valve spool 7. One end of the energy-storing elastic member 10 is fixedly connected to the fixing bolt 12. A first relief hole 11 is opened in the fixing bolt 12. Among them, the first elastic member 9 and the energy-storing elastic member 10 may both be springs.

[0037] It should be noted that when the first valve spool 7 is in the closed position, the other end of the energy-storing elastic member 10 does not abut against the first valve spool 7, and when the first valve spool 7 is in the open position, the other end of the energy-storing elastic member 10 begins to abut against the first valve spool 7, and as the first valve spool 7 continues to move forward from the open position, the first valve spool 7 compresses the energy-storing elastic member 10, causing the energy-storing elastic member 10 to elastically deform.

[0038] In this embodiment, as shown in FIGS. 5 to 7, the three-position solenoid valve 21 includes a second valve body 22, a second valve spool 27, a second elastic member 28, and an electromagnetic part 29. A second valve cavity 23 is provided within the second valve body 22, and a second liquid inlet 24 is provided at the front end of the second valve cavity 23. The second valve body 22 is provided with a second liquid outlet 25 and a third liquid outlet 26, which are respectively connected to the second valve cavity 23, arranged from front to rear. As a result, the second liquid inlet 24 can be connected to both the second liquid outlet 25 and the third liquid outlet 26 via the second valve cavity 23, and the hydraulic oil can enter the second valve cavity 23 via the second liquid inlet 24 and then flow out from the second liquid outlet 25 and the third liquid outlet 26, respectively.

[0039] The second valve spool 27 is located in the second valve cavity 23 and can move in the forward and backward directions of the second valve cavity 23. However, the second valve spool 27 is tightly fitted to the inner wall of the second valve cavity 23, preventing hydraulic oil from passing through.

[0040] The second elastic member 28 is used to hold the second valve spool 27 in a first position that blocks communication between the second liquid inlet 24 and the second and third liquid outlets 25 and 26. Referring to FIG. 5, at this time, the second liquid inlet 24 is not in communication with either the second liquid outlet 25 or the third liquid outlet 26. The second elastic member 28 may be a spring, and is specifically provided at the rear of the second valve cavity 23. One end of the spring is connected to the rear end of the second valve spool 27, and the other end is connected to the second valve body 22.

[0041] The electromagnetic unit 29 is provided at the rear end of the second valve body 22 and supplies two different magnitudes of electromagnetic force to drive the second valve spool 27 to move to either a second position, as shown in Figure 6, where the elastic force of the second elastic member 28 is overcome and the second liquid inlet 24 is connected only to the second liquid outlet 25, or to a third position, as shown in Figure 7, where the second liquid inlet 24 is connected to both the second liquid outlet 25 and the third liquid outlet 26. It should be noted that a magnetic component is fixed to the second valve spool 27, or a part of the second valve spool 27 is made of a magnetic material. Thus, when an electromagnetic force is generated in the solenoid part 29, the second valve body 22 is driven to move due to the attraction to the magnetic component or magnetic material. When a small electromagnetic force is generated in the solenoid part 29, the attraction force between the second valve spool 27 and the solenoid part 29 is small, and the second valve spool 27 can only move to the second position by overcoming the elastic force of the second elastic member 28. When a large electromagnetic force is generated in the solenoid part 29, the attraction force between the second valve spool 27 and the solenoid part 29 is large, and the second valve spool 27 can move to the third position by overcoming the elastic force of the second elastic member 28.

[0042] In this way, by the structural arrangement of the second valve body 22 and the arrangement of the second elastic member 28 and the solenoid portion, the second valve spool 27 can be switched between a first position in which the second inlet 24 is not in communication with either the second outlet 25 or the third outlet 26, a second position in which the second inlet 24 is in communication with only the second outlet 25, and a third position in which the second inlet 24 is in communication with both the second outlet 25 and the third outlet 26. This allows control of two different oil passages, i.e., control of the first connecting oil passage 41 and the second connecting oil passage 42, and is simpler in structure and easier to operate than multiple individual solenoid valves. The three-position solenoid valve 21 can control the pressure regulating valve 19 and the switching valve instead of multiple solenoid valves, simplifying the structure of the hydraulic control system, reducing the number of parts used, and lowering manufacturing costs. In addition, in this hydraulic control system, drive control of the pressure regulating valve 19 and the integrated switching / energy storing valve 20 can be achieved simply by inputting one control signal to the three-position solenoid valve 21, making operation easy.

[0043] As shown in Figures 5 to 7, a second relief hole 30 is formed in the second valve spool 27, and the rear end (tail end) of the second relief hole 30 extends from the rear end of the second valve body 22 to the outside of the second valve cavity 23. When the second valve spool 27 is located at the first position, the front end of the second relief hole 30 is connected to the second outlet port 25, and when the second valve spool 27 is located at the second or third position, the front end of the second relief hole 30 is not connected to either the second outlet port 25 or the third outlet port 26. In this way, when the second valve spool 27 moves from the second or third position to the first position, the hydraulic pressure in the first connecting oil passage 41 can be released through the second relief hole 30. In other words, the hydraulic pressure at the rear control port of the pressure regulating valve 19 is released, preventing the pressure regulating valve 19 from adjusting the hydraulic pressure in the oil supply passage 18, and further returning the hydraulic oil in the oil supply passage 18 to a low pressure state.

[0044] The number of second outlets 25 and third outlets 26 is at least two, and the second outlets 25 and third outlets 26 are arranged at equal intervals around the direction of movement of the second valve spool 27. That is, the second outlets 25 are arranged at equal intervals around the direction of movement of the second valve spool 27 in the second valve body 22, and the third outlets 26 are arranged at equal intervals around the direction of movement of the second valve spool 27 in the second valve body 22. In this way, it is possible to ensure that the second valve spool 27 receives a uniform force when the hydraulic oil flows out from the second outlets 25 and the third outlets 26, and further to extend the service life of the three-position solenoid valve 21. For example, as shown in Figures 5 to 7, the number of second outlets 25 and the number of third outlets 26 are both two, and the two second outlets 25 and the two third outlets 26 are respectively arranged symmetrically along the movement direction of the second valve spool 27. That is, one second outlet 25 and one third outlet 26 are arranged in the upper part of the second valve body 22, and the other second outlet 25 and the other third outlet 26 are arranged in the lower part of the second valve body 22.

[0045] In this embodiment, as shown in FIG. 1, the hydraulic control system further includes a mechanical oil pump 31, a filter 32 and a circulation oil passage 33.

[0046] The oil outlet end of the mechanical oil pump 31 communicates with the oil supply line 18, and the oil inlet end of the mechanical oil pump 31 communicates with the oil tank 34 via the filter 32. The mechanical oil pump 31 pumps the hydraulic oil in the oil tank 34 into the oil supply line 18 so that the hydraulic oil can circulate within the hydraulic control system. The filter 32 is a magnetic filter that can absorb iron filings in the hydraulic oil to keep the hydraulic oil clean. One end of the circulation oil passage 33 communicates with the oil supply passage 18, specifically, with the oil supply passage 18 between the mechanical oil pump 31 and the three-position solenoid valve 21, and the other end of the circulation oil passage 33 communicates with the oil inlet end of the mechanical oil pump 31. A first check valve 35 is provided in the circulation oil passage 33, which allows the hydraulic oil in the circulation oil passage 33 to flow only to the oil supply passage 18 via the first check valve 35 and prevents the hydraulic oil in the circulation oil passage 33 from flowing to the oil inlet end of the mechanical oil pump 31 via the first check valve 35, preventing the hydraulic oil in the oil supply passage 18 from returning to the oil tank 34 via the circulation oil passage 33. By providing the circulation oil passage 33, it is possible to still achieve circulation of the hydraulic oil even when the mechanical oil pump 31 is rotating in reverse, and it is possible to prevent the hydraulic oil in the oil supply passage 18 from being completely sucked up by the mechanical oil pump 31. Among them, the first check valve 35 may be a gravity type check valve.

[0047] As shown in FIG. 1, the hydraulic control system further includes an electric oil pump 36, a second check valve 37, and a refill oil passage 38.

[0048] One end of the replenishment oil passage 38 communicates with the oil tank 34 via the filter 32, and the other end of the replenishment oil passage 38 communicates with the cooling lubrication oil passage 16. The electric oil pump 36 and the second check valve 37 are provided in the replenishment oil passage 38. The oil inlet end of the electric oil pump 36 communicates with the oil tank 34 via the filter 32, and the oil outlet end of the electric oil pump 36 communicates with the cooling lubrication oil passage 16 via the second check valve 37. The hydraulic oil at the oil outlet end of the electric oil pump 36 can only flow to the cooling lubrication oil passage 16 via the second check valve 37, and the hydraulic oil in the cooling lubrication oil passage 16 is prevented from returning to the oil tank 34 via the replenishment oil passage 38. When the mechanical oil pump 31 does not operate, or when a large amount of oil or high hydraulic pressure is required in the cooling lubrication oil passage 16, the electric oil pump 36 can supply hydraulic oil to the cooling lubrication oil passage 16 via the replenishment oil passage 38. The second check valve 37 may be a gravity type check valve.

[0049] Additionally, as shown in FIG. 1, the hydraulic control system further includes a relief valve 39 and a cooler 40 .

[0050] The relief valve 39's inlet and control port both communicate with the cooling lubricant oil passage 16, and its outlet communicates with the oil tank 34. A fourth throttle member 53 is provided between the relief valve 39's inlet and the cooling lubricant oil passage 16 to control the amount of hydraulic oil entering the relief valve 39's inlet from the cooling lubricant oil passage 16. When the hydraulic pressure in the cooling lubricant oil passage 16 is greater than a predetermined value, the cooling lubricant oil passage 16 is connected to the oil tank 34 via the relief valve 39. When the hydraulic pressure in the cooling lubricant oil passage 16 is less than the predetermined value, the cooling lubricant oil passage 16 is disconnected from the oil tank 34. In this way, if the hydraulic pressure in the cooling lubricant oil passage 16 is too high, the relief valve 39 releases the pressure, thereby protecting the safety of the cooling lubricant oil passage 16. The predetermined value can be determined based on the structural conditions of the cooling lubricant oil passage 16 itself and the hydraulic pressure that needs to be discharged.

[0051] The cooler 40 is provided in the cooling lubrication oil passage 16 to cool the hydraulic oil in the cooling lubrication oil passage 16, thereby keeping the hydraulic oil at a low temperature and further advantageously cooling the components to be cooled in the hybrid system. The oil outlet end of the cooling lubrication oil passage 16 branches into multiple oil discharge branch passages, and the hydraulic oil is delivered to the components to be cooled and lubricated in the hybrid system through the oil discharge branch passages, and each oil discharge branch passage is provided with a throttle member to control the amount of hydraulic oil flowing through each oil discharge branch passage. In this embodiment, the oil outlet end of the cooling / lubricating oil passage 16 is divided into a first oil discharge branch passage 43, a second oil discharge branch passage 44, a third oil discharge branch passage 45, and a fourth oil discharge branch passage 46. The first oil discharge branch passage 43 is provided with a fifth throttle member 54, the second oil discharge branch passage 44 is provided with a sixth throttle member 55, the third oil discharge branch passage 45 is provided with a seventh throttle member 56, and the fourth oil discharge branch passage 46 is provided with an eighth throttle member 57. Of course, in other embodiments, the number of oil discharge branches may be other numbers, and is set specifically as needed.

[0052] In this embodiment, the operation process of the hydraulic control system for the hybrid transmission is as follows.

[0053] When the vehicle is driven only by the drive motor and there is little demand for cooling and lubrication, for example, when the weather is cold, the three-position solenoid valve 21 is not energized, the second valve spool 27 is in the first position, the mechanical oil pump 31 sends the hydraulic oil in the oil tank 34 into the oil supply line 18, and then enters the cooling and lubrication oil line 16 via the first oil supply line 18-1 and the pressure regulating valve 19, and finally the hydraulic oil is delivered to the components in the hybrid system that need to be cooled and lubricated by each oil discharge branch line, thereby realizing the role of cooling and lubrication. Since the hydraulic oil in the oil supply line 18 cannot enter the first connecting oil line 41 and the second connecting oil line 42 via the three-position solenoid valve 21, the integrated switching and energy storage valve 20 is closed, the clutch 47 is in the disengaged state, the pressure regulating valve 19 is not operated, and the hydraulic oil in the oil supply line 18 is in a low-pressure state.

[0054] When the vehicle is driven only by the drive motor and there is a high demand for cooling and lubricating effects, for example, when the engine drives a generator to generate electricity, the three-position solenoid valve 21 is energized, a predetermined electromagnetic force that is not fully open is generated in the solenoid part 29 by PWM control, and the second valve spool 27 is placed in the second position. At this time, the hydraulic oil in the oil supply line 18 can enter the first connecting oil line 41 via the three-position solenoid valve 21, and the pressure in the oil supply line 18 is increased via the pressure regulating valve 19, so that the hydraulic oil entering the cooling and lubricating oil line 16 also becomes high-pressure oil. Because the hydraulic oil in the oil supply line 18 cannot enter the second connecting oil line 42 via the three-position solenoid valve 21, the integrated switching and energy storage valve 20 is closed and the clutch 47 is in a disengaged state. When the three-position solenoid valve 21 is not energized, the second valve spool 27 moves from the second position to the first position, and the hydraulic oil in the oil supply line 18 cannot enter the first connecting oil line 41 through the three-position solenoid valve 21. The existing hydraulic oil in the first connecting oil line 41 flows into the oil tank 34 through the first relief hole 11, the pressure regulating valve 19 does not operate, and the hydraulic pressure in the oil supply line 18 returns to a low pressure state.

[0055] When it is necessary to drive the vehicle by the engine, the three-position solenoid valve 21 is energized, and the solenoid part 29 is fully opened or generates a fairly large electromagnetic force by PWM control, and further, when the second valve spool 27 is positioned at the third position, the hydraulic oil in the oil supply line 18 can enter the first connecting oil line 41 and the second connecting oil line 42 via the three-position solenoid valve 21, the integrated switching / energy storage valve 20 is opened, and the hydraulic oil in the oil supply line 18 is put into a high-pressure state due to pressure increase via the pressure regulating valve 19, and the hydraulic oil entering the cooling / lubrication oil line 16 and the drive oil line 17 also becomes high-pressure oil, and the high-pressure hydraulic oil drives the clutch 47 to engage. When the engine does not need to drive the vehicle and the three-position solenoid valve 21 is not energized, the second valve spool 27 moves from the third position to the first position, the hydraulic oil in the oil supply line 18 cannot enter the first connecting oil line 41 and the second connecting oil line 42 via the three-position solenoid valve 21, the switching / energy-storage integrated valve 20 is closed, the hydraulic oil already in the second connecting oil line 42 flows into the oil tank 34 after passing through the energy-storage flow path 6, the energy-storage cavity 8 and the first relief hole 11 in that order, the clutch 47 is disengaged, and the hydraulic oil already in the first connecting oil line 41 flows into the oil tank 34 via the second relief hole 30, and the hydraulic pressure in the oil supply line 18 is restored to a low pressure state.

[0056] When the amount of hydraulic oil in the cooling and lubricating oil passage 16 is insufficient, and the vehicle is parked and the vehicle air conditioning is not operating or the drive motor is not rotating, and cooling is required when the engine drives the generator to generate electricity, the electric oil pump 36 operates to send oil from the oil tank 34 to the cooling and lubricating oil passage 16, and the hydraulic oil is supplied to the parts in the hybrid system that need to be cooled and lubricated through each oil discharge branch, thereby achieving the role of cooling and lubricating.

[0057] When the vehicle is reversed, the mechanical oil pump 31 rotates in the reverse direction, the oil pressure in the oil supply line 18 becomes lower than the oil pressure in the circulation line 33, and the first check valve 35 opens, resulting in a loop being formed by the mechanical oil pump 31 and the first check valve 35, further reducing the impact of reduced system reliability due to the reverse rotation of the mechanical oil pump 31. In this case, the mechanical oil pump 31 does not supply oil to the oil supply line 18, and if cooling and lubrication are required, it is possible to supply hydraulic oil to the cooling and lubrication line 16 via the electric oil pump 36.

[0058] The above is merely a specific embodiment of the present invention, and those skilled in the art can make other improvements or modifications based on the above teachings of the present invention. Those skilled in the art should understand that the above specific description is only for better understanding of the present invention, and the protection scope of the present invention is subject to the protection scope of the claims. [Explanation of symbols]

[0059] 1 First valve body, 2 First valve cavity, 3 Drive port, 4 First liquid inlet, 5 First liquid outlet, 6 Energy storage passage, 7 First valve spool, 8 Energy storage cavity, 9 First elastic member, 10 Energy storage elastic member, 11 First relief hole, 12 Fixing bolt, 13 Connecting groove, 14 First accommodation cavity, 15 Second accommodation cavity, 16 Cooling and lubricating oil passage, 17...drive oil passage, 18...oil supply passage, 18-1...first oil supply passage, 18-2...second oil supply passage, 18-3...third oil supply passage, 18-4...fourth oil supply passage, 19...pressure regulating valve, 20...integrated switching and energy storage valve, 21...3-position solenoid valve, 22...second valve body, 23...second valve cavity, 24...second liquid inlet, 25...second liquid outlet, 26...third liquid outlet, 27... Second valve spool, 28...second elastic member, 29...electromagnetic part, 30...second relief hole passage, 31...mechanical oil pump, 32...filter, 33...circulation oil passage, 34...oil tank, 35...first check valve, 36...electric oil pump, 37...second check valve, 38...replenishment oil passage, 39...relief valve, 40...cooler, 41...first connecting oil passage, 42...second connecting oil passage, 43...First oil discharge branch passage, 44...Second oil discharge branch passage, 45...Third oil discharge branch passage, 46...Fourth oil discharge branch passage, 47...Clutch, 48...Sensor, 49...Wheel, 50...First throttling member, 51...Second throttling member, 52...Third throttling member, 53...Fourth throttling member, 54...Fifth throttling member, 55...Sixth throttling member, 56...Seventh throttling member, 57...Eighth throttling member.

Claims

1. A hydraulic control system for a hybrid transmission, comprising a cooling and lubricating oil passage, a drive oil passage, an oil supply passage, a pressure regulating valve, a three-position solenoid valve, and a switching and energy storage integrated valve; the oil supply passage communicates with the inlet of the pressure regulating valve, a front control port of the pressure regulating valve, the inlet of the three-position solenoid valve, and the inlet of the integrated switching and energy storage valve, respectively, and is for supplying hydraulic oil; a second outlet of the three-position solenoid valve communicates with the rear control port of the pressure regulating valve, and a third outlet of the three-position solenoid valve communicates with the drive port of the integrated switching and energy storage valve; the cooling and lubricating oil passage communicates with the outlet of the pressure regulating valve and is for feeding hydraulic oil to a hybrid system; and the drive oil passage communicates with the outlet of the integrated switching and energy storage valve and is for supplying high-pressure oil to a clutch, a hydraulic control system for a hybrid transmission, characterized in that when an inlet of the three-position solenoid valve does not communicate with either a second outlet of the three-position solenoid valve or a third outlet of the three-position solenoid valve, the hydraulic oil in the fuel supply line is in a low-pressure state and the integrated switching and energy-storage valve is closed; when an inlet of the three-position solenoid valve communicates only with the second outlet of the three-position solenoid valve, the hydraulic oil in the fuel supply line is in a high-pressure state and the integrated switching and energy-storage valve is closed; and when an inlet of the three-position solenoid valve communicates with both the second outlet of the three-position solenoid valve and the third outlet of the three-position solenoid valve, the hydraulic oil in the fuel supply line is in a high-pressure state and the integrated switching and energy-storage valve is opened.

2. The integrated switching and energy storage valve includes a first valve body, a first valve spool, a first elastic member, and an energy storage elastic member, a first valve cavity is provided within the first valve body, the drive port is provided at a rear end of the first valve body and communicates with the first valve cavity, and the first valve body is provided with a first liquid inlet and a first liquid outlet, each communicating with the first valve cavity, and an energy storage flow path communicating with the first liquid outlet, the first valve spool is located in the first valve cavity and is piston-movable along the front-rear direction of the first valve cavity; an energy storage cavity communicating with the energy storage passage is formed between a front portion of the first valve spool and an inner cavity wall of the first valve cavity; and the energy storage cavity expands along the moving direction of the first valve spool when the first valve spool moves forward; the first elastic member is for holding the first valve spool in a blocking position where communication between the first liquid inlet and the first liquid outlet is blocked, and when pressurized driving fluid enters through the drive port, the first valve spool is driven to overcome the elastic force of the first elastic member and move forward to an open position where communication between the first liquid inlet and the first liquid outlet is established, 2. The hydraulic control system for a hybrid transmission according to claim 1, wherein the energy-storing elastic member is provided in the first valve cavity on the front side of the energy-storing cavity, and serves to supply an elastic force to the first valve spool that suppresses expansion of the energy-storing cavity.

3. 3. The hydraulic control system for a hybrid transmission according to claim 2, wherein a connecting groove or a connecting hole is formed in the first valve spool, and when the first valve spool is positioned in the open position, the connecting groove or the connecting hole connects the first fluid inlet and the first fluid outlet.

4. 4. The hydraulic control system for a hybrid transmission according to claim 2 or 3, wherein a first relief hole is formed in a front end of the first valve body, and the first relief hole is in communication with the energy storage cavity through a gap between the first valve spool and the first valve body.

5. The integrated switching and energy storage valve further includes a fixing bolt, 5. The hydraulic control system for a hybrid transmission according to claim 4, wherein the fixing bolt is inserted and fixed into the first valve cavity from a front end of the first valve body, a first accommodating cavity is formed in a front portion of the first valve spool, and a second accommodating cavity communicating with the first accommodating cavity is formed in a central portion of the first valve spool, the leading end of the fixing bolt is inserted from the first accommodating cavity into the second accommodating cavity, the first elastic member is located in the second accommodating cavity, one end of the first elastic member abuts against the leading end of the fixing bolt and the other end of the first elastic member abuts against the first valve spool, the energy-storing elastic member is located in the first accommodating cavity, and one end of the energy-storing elastic member is fixedly connected to the fixing bolt, and the first relief hole is opened in the fixing bolt.

6. the three-position solenoid valve includes a second valve body, a second valve spool, a second elastic member, and an electromagnetic portion; a second valve cavity is provided within the second valve body, a second liquid inlet is provided at a front end of the second valve cavity, and a second liquid outlet and a third liquid outlet are provided in the second valve body in this order from front to rear, the second liquid outlet and the second valve cavity being respectively connected to the second valve cavity; the second valve spool is located in the second valve cavity and is piston-movable along the front-rear direction of the second valve cavity; the second elastic member is for holding the second valve spool in a first position at which communication between the second liquid inlet and the second and third liquid outlets is blocked, 2. The hydraulic control system for a hybrid transmission according to claim 1, wherein the electromagnetic unit is provided at a rear end of the second valve body and supplies two types of electromagnetic forces of different magnitudes to drive the second valve spool to move to a second position where the second fluid inlet is connected only to the second fluid outlet by overcoming the elastic force of the second elastic member, or to a third position where the second fluid inlet is connected to both the second fluid outlet and the third fluid outlet.

7. 7. The hydraulic control system for a hybrid transmission according to claim 6, wherein a second relief hole is formed in the second valve spool, and a rear end of the second relief hole extends from a rear end of the second valve body to an outside of the second valve cavity, and a front end of the second relief hole communicates with the second outlet port when the second valve spool is located at the first position.

8. Further comprising a mechanical oil pump, a filter and a circulation oil passage; 2. The hydraulic control system for a hybrid transmission according to claim 1, wherein an oil outlet end of the mechanical oil pump communicates with the oil supply line, an oil inlet end of the mechanical oil pump communicates with an oil tank via the filter, one end of the circulation oil line communicates with the oil supply line, and the other end of the circulation oil line communicates with the oil inlet end of the mechanical oil pump, and a first check valve is provided in the circulation oil line, so that hydraulic oil in the circulation oil line can only flow to the oil supply line via the first check valve.

9. further including an electric oil pump and a second check valve; 9. The hydraulic control system for a hybrid transmission according to claim 8, wherein an oil inlet end of the electric oil pump communicates with the oil tank via the filter, an oil outlet end of the electric oil pump communicates with the cooling lubrication oil passage via the second check valve, and the hydraulic oil at the oil outlet end of the electric oil pump is allowed to flow only to the cooling lubrication oil passage via the second check valve.

10. Further comprising a relief valve and a cooler; The inlet of the relief valve and the control port of the relief valve are both connected to the cooling lubricant oil passage, and the outlet of the relief valve is connected to an oil tank, and when the oil pressure in the cooling lubricant oil passage is greater than a predetermined value, the cooling lubricant oil passage is connected to the oil tank, and when the oil pressure in the cooling lubricant oil passage is not greater than the predetermined value, the cooling lubricant oil passage is disconnected from the oil tank, The hydraulic control system for a hybrid transmission as described in claim 1, characterized in that the cooler is provided in the cooling lubrication oil passage and is for cooling the hydraulic oil in the cooling lubrication oil passage, the oil outlet end of the cooling lubrication oil passage is divided into a plurality of oil discharge branch passages, and a throttling member is provided in each of the oil discharge branch passages.

Images