Piston cooling nozzle, engine and vehicle

Abstract

The present invention relates to engine cooling and lubrication technology, and in particular to a piston cooling nozzle, an engine and a vehicle. The piston cooling nozzle includes a housing, a main valve core and a control valve core. The interior of the housing is provided with a first inner cavity, a second inner cavity and an oil drain channel. The first inner cavity is connected to the second inner cavity through the oil drain channel. The first inner cavity is provided with a lubricating oil inlet. The side wall of the first inner cavity is connected with a lubricating oil channel. The other end of the lubricating oil channel is connected with a cooling nozzle. The side wall of the second inner cavity is provided with an intercooler rear air intake port. The second inner cavity is provided with a lubricating oil outlet. The control valve core is movably arranged in the second inner cavity. The main valve core is movably arranged in the first inner cavity. The flow rate from the first inner cavity to the lubricating oil channel is positively correlated with the pressure of the intercooler rear air intake port entering the intercooler rear air intake port. The piston cooling nozzle of the present invention can spray the required lubricating oil according to the load conditions of the engine.

Description

Technical Field

[0001] The present invention relates to engine cooling and lubrication technology, and particularly relates to a piston cooling nozzle, an engine and a vehicle. Background Art

[0002] Under the existing technology, the flux of the lubricating oil flow sprayed by the nozzle is only related to the pressure of the lubricating oil. When the engine operates at low speed and high load or high speed and low load, there are problems of insufficient or excessive fuel injection of the piston cooling nozzle, which affects piston cooling and is likely to cause faults such as cylinder scoring and melting of the piston crown. Summary of the Invention

[0003] The purpose of the present invention is to at least solve the problem that the flow rate of the lubricating oil sprayed by the piston cooling nozzle cannot be regulated. This purpose is achieved by the following technical solutions:

[0004] A first aspect of the present invention provides a piston cooling nozzle, including:

[0005] A housing, wherein a first inner cavity, a second inner cavity and an oil drain passage are arranged inside the housing, and the first inner cavity is communicated with the second inner cavity through the oil drain passage;

[0006] The first inner cavity is provided with a lubricating oil inlet, and a lubricating oil passage is communicated with the side wall of the first inner cavity;

[0007] The side wall of the second inner cavity is provided with an intake port after intercooling, and the second inner cavity is provided with a lubricating oil outlet;

[0008] A cooling nozzle head, which is communicated with the lubricating oil passage;

[0009] A control valve core, which is movably arranged in the second inner cavity, and the control valve core is used to control the flow rate of the lubricating oil in the oil drain passage;

[0010] A main valve core, which is movably arranged in the first inner cavity, and the main valve core is used to regulate the flow rate of the lubricating oil flowing from the first inner cavity to the lubricating passage. The flow rate of the lubricating oil flowing from the first inner cavity to the lubricating oil passage is positively correlated with the pressure of the intake air after intercooling entering from the intake port after intercooling.

[0011] According to the piston cooling nozzle of the present invention, the flow rate of the lubricating oil of the cooling nozzle is ultimately positively correlated with the pressure of the intake air after intercooling, and the intake air pressure after intercooling is related to the engine load. Therefore, the flow rate of the cooling nozzle is associated with the engine load. When the engine load increases, the cooling amount required by the piston also increases. At this time, due to the increase in the pressure of the intake air after intercooling, the flow rate of the lubricating oil controlling the cooling nozzle increases, increasing the ejection amount of the lubricating oil of the piston cooling nozzle to meet the requirements of the engine. Conversely, when the engine load decreases, the cooling amount required by the piston decreases. At this time, due to the decrease in the intake air pressure after intercooling, the flow rate of the lubricating oil of the cooling nozzle decreases, reducing the ejection amount of the lubricating oil of the piston cooling nozzle, saving the usage amount of the lubricating oil, and reducing the waste of the lubricating oil.

[0012] In addition, the piston cooling nozzle according to the present invention may further have the following additional technical features:

[0013] In some embodiments of the present invention, an oil storage cavity is provided in the first inner cavity, the oil storage cavity is used for storing lubricating oil, and the lubricating oil in the oil storage cavity is used to drive the main valve core to move relative to the first inner cavity.

[0014] In some embodiments of the present invention, a through hole is axially provided in the main valve core, and the oil storage cavity is communicated with the lubricating oil inlet through the through hole.

[0015] In some embodiments of the present invention, the piston cooling nozzle further includes an elastic member, the elastic member is disposed in the first inner cavity, and the elastic member cooperates with the inner wall of the first inner cavity and the main valve core respectively. The resilience of the elastic member is used to drive the main valve core to move in a direction close to the lubricating oil inlet.

[0016] In some embodiments of the present invention, a buffer cavity is further provided between the lubricating oil passage and the cooling nozzle.

[0017] In some embodiments of the present invention, a return spring is further provided in the second inner cavity. One end of the return spring is fixedly provided on a side of the second inner cavity away from the intake air port after intercooling, and the other end of the return spring is connected to the control valve core. The resilience of the return device is used to drive the control valve core to move in a direction close to the intake air port after intercooling.

[0018] In some embodiments of the present invention, the number of the lubricating oil passages is at least two.

[0019] In some embodiments of the present invention, an axial step end face for limiting the main valve core is provided in the first inner cavity.

[0020] A second aspect of the present invention provides an engine including the above-mentioned piston cooling nozzle.

[0021] A third aspect of the present invention provides a vehicle, including the above-mentioned engine. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] By reading the following detailed description of the preferred embodiments, various other advantages and benefits will become clear to those of ordinary skill in the art. The drawings are only for the purpose of showing the preferred embodiments and are not considered as a limitation of the present invention. Moreover, throughout the drawings, the same reference numerals are used to represent the same components. In the drawings:

[0023] Figure 1 A schematic cross-sectional structure diagram of a piston cooling nozzle according to an embodiment of the present invention is schematically shown.

[0024] The reference numerals are as follows:

[0025] 100 is the piston cooling nozzle;

[0026] 10 is the housing, 11 is the first inner cavity, 111 is the lubricating oil passage, 112 is the buffer cavity, 113 is the lubricating oil inlet, 114 is the oil storage cavity, 12 is the second inner cavity, 121 is the intake port after intercooling, 122 is the lubricating oil outlet, 13 is the oil drain passage;

[0027] 20 is the main spool valve, 21 is the through hole;

[0028] 30 is the control spool valve;

[0029] 40 is the cooling nozzle;

[0030] 50 is the return spring;

[0031] 60 is the elastic member. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0032] The exemplary embodiments of the present disclosure will be described in more detail below with reference to the drawings. Although the exemplary embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure can be implemented in various forms and should not be limited by the embodiments set forth herein. On the contrary, these embodiments are provided so that the present disclosure can be more thoroughly understood and the scope of the present disclosure can be fully conveyed to those skilled in the art.

[0033] It should be understood that the terms used herein are for the purpose of describing particular example embodiments only and are not intended to be limiting. Unless the context clearly dictates otherwise, the singular forms "a", "an", and "the" as used herein may also include the plural forms. The terms "comprising", "including", "containing", and "having" are inclusive and thus specify the presence of stated features, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, steps, operations, elements, components, and / or combinations thereof. The method steps, processes, and operations described herein are not to be construed as necessarily requiring their performance in the particular order described or illustrated, unless explicitly stated as an order of performance. It should also be understood that additional or alternative steps may be used.

[0034] Although the terms first, second, third, etc. may be used herein to describe multiple elements, components, regions, layers, and / or sections, these elements, components, regions, layers, and / or sections should not be limited by these terms. These terms may be used only to distinguish one element, component, region, layer, or section from another. Unless the context clearly indicates otherwise, terms such as "first", "second", and other numerical terms when used herein do not imply an order or sequence. Thus, the first element, component, region, layer, or section discussed below may be referred to as a second element, component, region, layer, or section without departing from the teachings of the example embodiments.

[0035] For ease of description, spatial relative relationship terms may be used herein to describe the relationship of one element or feature shown in the figures to another element or feature, such relative relationship terms such as "inner", "outer", "inside", "outside", "below", "beneath", "above", "over" and the like. Such spatial relative relationship terms are intended to include different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is flipped, an element described as "below" or "beneath" another element or feature will then be oriented "above" or "over" the other element or feature. Thus, the example term "below" can include both an orientation above and below. The device may be otherwise oriented (rotated 90 degrees or in other directions) and the spatial relative relationship descriptors used herein are to be interpreted accordingly.

[0036] As Figure 1 shown, according to an embodiment of the present invention, a piston cooling nozzle 100 is provided, wherein the piston cooling nozzle 100 includes a housing 10, a main spool 20, and a control spool 30, and the internal structure of the housing 10 is divided into a first inner cavity 11, a second inner cavity 12, and an oil drain passage 13.

[0037] The first inner cavity 11 and the second inner cavity 12 are connected through an oil drain channel 13, and the oil drain channel 13 allows lubricating oil to flow from the first inner cavity 11 to the second inner cavity 12. A lubricating oil inlet 113 is provided in the first inner cavity 11, and the lubricating oil enters the first inner cavity 11 from the lubricating oil inlet 113.

[0038] A lubricating oil passage 111 is connected to the side wall of the first inner cavity 11, and the other end of the lubricating oil passage 111 is connected to a cooling spray head 40. The lubricating oil flows from the first inner cavity 11 to the lubricating oil passage 111, and the lubricating oil passage 111 then transports the lubricating oil to the cooling spray head 40. The cooling spray head 40 sprays the lubricating oil into the piston through a pipeline, and the piston is cooled.

[0039] A movable main valve core 20 is also provided in the first inner cavity 11. The main valve core 20 makes a reciprocating motion under the influence of the pressure of the lubricating oil. When the main valve core 20 makes a reciprocating motion, the opening degree of the lubricating oil passage 111 can be adjusted, and the flow rate of the lubricating oil passing through the lubricating oil passage 111 is adjusted. Then, the amount of the lubricating oil sprayed by the cooling spray head 40 is also adjusted. However, the movement of the main valve core 20 is passive, mainly making a reciprocating movement according to the change in the pressure difference between the pressure of the lubricating oil in the first inner cavity 11 and the pressure in the lubricating oil inlet 113. The oil drain channel 13 can control the pressure of the lubricating oil in the first inner cavity 11. The oil drain channel 13 transports the lubricating oil from the first inner cavity 11 to the second inner cavity 12, but the flow rate of the oil drain channel 13 is controlled by a control valve core 30.

[0040] The control valve core 30 is movably arranged in the second inner cavity 12. A post-intercooling air inlet 121 is provided on the side wall of the second inner cavity 12, and a lubricating oil outlet 122 is provided in the second inner cavity 12. Due to the influence of the air pressure of the post-intercooling air transported in the post-intercooling air inlet 121, the control valve core 30 makes a reciprocating motion in the second inner cavity 12. Then, the opening degree of the oil drain channel 13 changes with the movement of the control valve core 30, and the flow rate of the lubricating oil flowing out from the lubricating oil outlet 122 also changes with the movement of the control valve core 30. At the same time, the flow rate of the lubricating oil flowing from the first inner cavity 11 to the lubricating oil passage 111 is positively correlated with the pressure of the post-intercooling air entering from the post-intercooling air inlet 121.

[0041] For the piston cooling nozzle 100 according to this embodiment, the flow rate of the lubricating oil in the cooling nozzle 40 is ultimately positively correlated with the pressure of the intake air after intercooling, and the intake air pressure after intercooling is related to the engine load. Therefore, the flow rate of the cooling nozzle 40 is associated with the engine load. When the engine load increases, the cooling amount required by the piston also increases. At this time, due to the increase in the pressure of the intake air after intercooling, the flow rate of the lubricating oil in the cooling nozzle 40 is increased, and the ejection amount of the lubricating oil of the piston cooling nozzle 100 is increased to meet the engine's requirements. Conversely, when the engine load decreases, the cooling amount required by the piston decreases. At this time, due to the decrease in the intake air pressure after intercooling, the flow rate of the lubricating oil in the cooling nozzle 40 is reduced, and the ejection amount of the lubricating oil of the piston cooling nozzle 100 is reduced, saving the usage amount of the lubricating oil and reducing the waste of the lubricating oil.

[0042] It can be understood that an axial stepped end face is provided in the first inner cavity 11 for limiting the main spool 20.

[0043] There may be two axial stepped end faces in the first inner cavity 11. The first axial stepped end face is close to the lubricating oil inlet 113, and the first axial stepped end face has a chamfer structure. The top end of the main spool 20 is also provided with a chamfer structure that matches the first axial stepped end face. When the lubricating oil enters from the lubricating oil inlet 113, the chamfer structure plays a guiding role, enabling the lubricating oil to flow stably into the first inner cavity 11. Another function of the first axial stepped end face is to limit the main spool 20 to prevent the main spool 20 from passing through the lubricating oil inlet 113.

[0044] The second axial stepped end face is provided at the position where the first inner cavity 11 is close to the second inner cavity 12. The second axial stepped end face also limits the main spool 20. At the same time, the space between the second axial stepped end face and the bottom of the first inner cavity 11 is the oil storage cavity 114, which means that the distance between the second axial stepped end face and the bottom of the first inner cavity 11 determines the size of the oil storage cavity 114. The size of the oil storage cavity 114 can affect the reciprocating movement rate of the main spool 20. Therefore, the setting of the second axial stepped end face is designed according to the different lubricating oil ejection amounts required by different engines.

[0045] Therefore, it can be understood that the first inner cavity 11 is provided with an oil storage cavity 114, and the purpose is to use the pressure of the lubricating oil stored in the oil storage cavity 114 to adjust the reciprocating movement of the main spool 20.

[0046] It can be understood that the main spool 20 is axially provided with a through hole 21. The through hole 21 can enable the lubricating oil to flow from the top of the main spool 20 to the oil storage cavity 114 to control the lubricating oil pressure in the oil storage cavity 114. The aperture of the through hole 21 is designed according to the lubricating oil injection amount required by different engines.

[0047] It can be understood that the number of lubricating oil channels 111 is at least two. The positions and numbers of the lubricating oil channels 111 are calculated. Different engines need to set different numbers of lubricating oil channels 111 to meet the injection volume of the lubricating oil.

[0048] Taking two lubricating oil channels 111 as an example, there are axial stepped end faces on the valve body of the main spool 20. Therefore, there are protruding parts and groove parts on the valve body of the main spool 20. When one protruding part blocks one lubricating oil channel 111, the other lubricating oil channel 111 corresponds to the groove part of the main spool 20. This not only means reducing the flow rate of the lubricating oil flowing into the lubricating oil channel 111, reducing the ejection volume of the lubricating oil of the piston cooling nozzle 100, saving the usage amount of the lubricating oil, but also reducing the waste of the lubricating oil.

[0049] Another situation is that both of the two lubricating oil channels 111 correspond to the groove part of the main spool 20. Then the flow rate of the lubricating oil in the lubricating oil channel 111 will increase, increasing the ejection volume of the lubricating oil of the piston cooling nozzle 100 to meet the requirements of the engine. Therefore, the up and down movement of the main spool 20 determines the opening degree of the lubricating oil channel 111 and controls the flow rate of the lubricating oil flowing to the cooling nozzle 40.

[0050] Specifically, a buffer chamber 112 is also provided between the lubricating oil channel 111 and the cooling nozzle 40. Since the displacement of the main spool 20 is constantly changing, the flow rate of the lubricating oil flowing into the lubricating oil channel 111 is unstable, resulting in an unstable ejection volume of the lubricating oil ejected at the cooling nozzle 40. By setting a buffer chamber 112, the lubricating oil first enters the buffer chamber 112. When the buffer chamber 112 is full of lubricating oil, it will flow into the cooling nozzle 40. In this way, the lubricating oil ejected by the cooling nozzle 40 can be relatively stable, playing a protective role for the piston.

[0051] It can be understood that a return spring 50 is also provided in the second inner cavity 12. One end of the return spring 50 is fixedly arranged on the side of the second inner cavity 12 away from the after-cooled intake port 121, and the other end of the return spring 50 is arranged to be connected to the control spool 30 at the other end. When the after-cooled intake air becomes smaller, the pressure at the after-cooled intake port 121 becomes smaller, and the spring force will push the control spool 30 to move towards the position of the after-cooled intake port 121. What can push the control spool 30 to move can be but is not limited to a spring.

[0052] It can be understood that an elastic member 60 is also provided in the first inner cavity 11, and the elastic member 60 is respectively engaged with the inner wall of the first inner cavity 11 and the main spool valve 20. The resilience of the elastic member 60 is used to drive the main spool valve 20 to move in the direction close to the lubricating oil inlet 113 to assist the lubricating oil pressure in the auxiliary oil storage cavity 114 to move the main spool valve 20. The spring force of the return spring 50 in the second inner cavity 12 is opposite to the intake pressure of the post-intercooler intake air, and the resilience provided by the elastic member 60 in the first inner cavity 11 is in the same direction as the pressure provided by the lubricating oil in the oil storage cavity 114. The elastic member in the first inner cavity 11 can be a spring or a spring sheet.

[0053] In a specific embodiment, the housing 10 of the piston cooling nozzle 100 is cylindrical. The interior of the housing 10 is divided into a first inner cavity 11 and a second inner cavity 12, and the first inner cavity 11 and the second inner cavity 12 are communicated through an oil drain passage 13. A lubricating oil inlet 113 is provided at the top of the first inner cavity 11. Two lubricating oil channels 111 are provided on the side wall of the first inner cavity 11. The other end of the lubricating oil channel 111 is connected to a buffer cavity 112, and the buffer cavity 112 is connected to a cooling nozzle 40. The lubricating oil channels 111 are arranged vertically along the direction of gravity.

[0054] The inner wall of the first inner cavity 11 is axially stepped, with a total of 2 axially stepped end faces. The first axially stepped end face is close to the lubricating oil inlet 113 and is chamfered. The second axially stepped end face is close to the second inner cavity 12. There is a certain distance between the second axially stepped end face and the bottom of the first inner cavity 11. A storage cavity 114 is formed between the second axially stepped end face and the bottom of the first inner cavity 11.

[0055] The main spool valve 20 is arranged in the first inner cavity 11 and makes a reciprocating up and down movement. The main spool valve 20 is also cylindrical, and the valve body of the main spool valve 20 is also stepped. Therefore, the valve body of the main spool valve 20 has two parts: a convex part and a concave part. The specific structure of the main spool valve 20 is the valve body head, followed by the middle part of the valve body composed of three grooves and two protrusions, and finally the bottom of the valve body with a thicker diameter. The arrangement of the protrusions and grooves in the middle part of the valve body is groove, protrusion, groove, protrusion, and finally groove. The distance between the two protrusions in the middle part of the valve body is not equal to the distance between the upper and lower lubricating oil channels 111. An elastic member 60 is provided between the bottom of the main spool valve 20 and the bottom of the first inner cavity 11.

[0056] The control spool valve 30 is arranged in the second inner cavity 12 and makes a reciprocating left and right movement. The oil drain passage 13 is arranged on the left side in the axial direction. The control spool valve 30 is also stepped, including three protrusions and two grooves. The right end of the control spool valve 30 is connected to a return spring 50, and the other end of the return spring 50 is fixed on the left side wall of the second inner cavity 12. A lubricating oil outlet 122 is provided at the bottom of the second inner cavity 12 along the axial position.

[0057] It can be understood that the moving direction of the main spool valve 20 is up and down in the first inner cavity 11 along the direction of gravity, and the moving direction of the control spool valve 30 is left and right in the second inner cavity 12 perpendicular to the direction of gravity.

[0058] When the engine load increases, the pressure of the intake air after intercooling increases, the control spool valve 30 moves to the right, the opening degree of the oil drain passage 13 increases, the lubricating oil drain accelerates, and the pressure in the oil storage cavity 114 decreases. At this time, the pressure at the bottom of the main spool valve 20 decreases, the main spool valve 20 moves downward, the opening degree of the lubricating oil passage 111 increases, that is, the flow rate of the cooling nozzle 40 increases, and the piston cooling effect is enhanced.

[0059] When the engine load decreases, the pressure of the intake air after intercooling decreases, the control spool valve 30 moves to the left, the opening degree of the oil drain passage 13 decreases, the lubricating oil drain slows down, and the pressure in the oil storage cavity 114 increases. At this time, the pressure at the bottom of the main spool valve 20 increases, the main spool valve 20 moves upward, the opening degree of the lubricating oil passage 111 decreases, the flow rate of the lubricating oil passage 111, that is, the flow rate of the cooling nozzle 40 decreases, and the piston cooling amount decreases.

[0060] When the engine runs stably, the pressure of the intake air after intercooling is stable, the position of the control spool valve 30 is fixed. At this time, the flow rates of the lubricating oil inlet 113, the oil storage cavity 114 and the lubricating oil outlet 122 are in a stable state, the position of the main spool valve 20 remains stable, and the flow rate of the lubricating oil passage 111 does not change.

[0061] The embodiment of the present invention also provides an engine, including the piston cooling nozzle 100 as described above.

[0062] It can be understood that the cooling nozzle 40 on the piston cooling nozzle 100 is connected to the piston of the engine through a pipeline to provide the lubricating oil required for piston cooling.

[0063] The embodiment of the present invention also provides a vehicle, including the engine as described above.

[0064] The above is only the preferred specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any changes or substitutions that can be easily thought of by those skilled in the art within the technical scope disclosed by the present invention should be covered by the protection scope of the present invention. Therefore, the protection scope of the present invention should be subject to the protection scope of the claims.

Claims

1. A piston cooling nozzle, characterized in that: include: A housing, wherein a first inner cavity, a second inner cavity and an oil drain passage are provided inside the housing, and the first inner cavity is connected to the second inner cavity through the oil drain passage; The first inner cavity is provided with a lubricating oil inlet, and the side wall of the first inner cavity is connected with a lubricating oil channel; An intercooler rear air inlet is provided on the side wall of the second inner cavity, and a lubricating oil outlet is provided in the second inner cavity; A cooling nozzle, the cooling nozzle is in communication with the lubricating oil passage; a control valve core, the control valve core being movably disposed in the second inner cavity, the control valve core being used to control the flow rate of lubricating oil in the oil drain channel; a main valve core, the main valve core being movably disposed in the first inner cavity, the main valve core being used to adjust the flow rate of lubricating oil from the first inner cavity to the lubricating oil passage, the flow rate of lubricating oil from the first inner cavity to the lubricating oil passage being positively correlated with the pressure of the intercooler rear intake air entering the intercooler rear intake port; Among them, the first inner cavity is provided with an oil storage cavity, which is used to store lubricating oil, and the lubricating oil in the oil storage cavity is used to drive the main valve core to move relative to the first inner cavity; the main valve core is provided with a through hole along its axial direction, and the oil storage cavity is connected with the lubricating oil inlet through the through hole; the piston cooling nozzle also includes an elastic member, which is arranged in the first inner cavity, and the elastic member is respectively matched with the inner wall of the first inner cavity and the main valve core, and the rebound force of the elastic member is used to drive the main valve core to move in a direction close to the lubricating oil inlet; a buffer cavity is also provided between the lubricating oil channel and the cooling nozzle; a return spring is also provided in the second inner cavity, one end of the return spring is fixedly arranged on a side of the second inner cavity away from the intercooler rear air intake port, and the other end of the return spring is connected to the control valve core, and the rebound force of the return spring is used to drive the control valve core to move toward a side close to the intercooler rear air intake port.

2. The piston cooling nozzle according to claim 1, characterized in that The number of the lubricating oil passages is at least two.

3. The piston cooling nozzle according to claim 1, characterized in that: An axial step end surface for limiting the position of the main valve core is arranged in the first inner cavity.

4. An engine, characterized in that: The engine comprises a piston cooling jet according to any one of claims 1-3.

5. A vehicle, characterized in that: Comprising an engine as claimed in claim 4.

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