CN215804761U - Pilot valve and two-stage variable displacement engine oil pump control system thereof - Google Patents
Pilot valve and two-stage variable displacement engine oil pump control system thereof Download PDFInfo
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- CN215804761U CN215804761U CN202122166410.1U CN202122166410U CN215804761U CN 215804761 U CN215804761 U CN 215804761U CN 202122166410 U CN202122166410 U CN 202122166410U CN 215804761 U CN215804761 U CN 215804761U
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Abstract
A pilot valve and a control system of a secondary variable displacement oil pump thereof comprise a single-action cavity feedback variable displacement oil pump, an oil outlet of the pump, a main oil duct, an oil pan, a switch electromagnetic valve and the pilot valve. The single-acting cavity feedback variable displacement oil pump comprises a feedback pressure oil cavity; the pilot valve comprises a valve sleeve, a valve core and a spring; the valve sleeve is provided with a feedback oil passage interface, a main cavity, a first pressure control cavity, a second pressure control cavity and a pressure relief port. The engine oil flowing into the first pressure control cavity and the second pressure control cavity can generate oil pressure opposite to the direction of spring force applied to the valve core by a spring on the valve core, and the valve core can axially move in the main cavity under the action of the spring force and the oil pressure, so that the feedback oil passage interface is alternatively communicated with the pressure relief port or the first pressure control cavity; a port P of the switching electromagnetic valve is communicated with the main oil duct, a port T is communicated with the oil pan, and a port A is communicated with the port P or the port T alternatively along with switching of a switching state. The single-action cavity feedback variable-displacement oil pump can realize a two-stage variable-displacement function.
Description
Technical Field
The utility model relates to the lubrication technology of an internal combustion engine, in particular to the control technology of a variable displacement oil pump.
Background
Conventional oil pumps include two variable forms, single acting cavity feedback and double acting cavity feedback. The feedback of the single-acting cavity can be designed into a primary variable displacement mode, or an MAP control mode can be realized through an electro-hydraulic proportional valve; the double acting cavity feedback may be designed in a two-stage variable displacement mode.
In order to enable the single-acting cavity feedback variable displacement oil pump to realize two-stage variable displacement, some manufacturers have proposed a scheme of adding a switching electromagnetic valve and a pilot valve to the structure of the single-acting cavity feedback variable displacement oil pump. Fig. 1 and 2 respectively show two structures of prior pilot valves for enabling a single-acting-chamber feedback variable displacement oil pump to realize a two-stage variable displacement function.
The pilot valve 91 shown in fig. 1 includes a valve housing 911, a valve spool 912, and a spring 913, a spring chamber 915 is provided between one end of the valve spool 912 connected to the spring 913 and the valve housing 911, a first pressure control chamber 916 is provided between the other end of the valve spool 912 and the valve housing 911, and a second pressure control chamber 917 is provided between the middle of the valve spool 912 and the inner wall of the valve housing 911. The pilot valve has large volume and not compact structure.
Fig. 2 shows pilot valve 92 including a valve sleeve 921, a valve spool 922, and a spring 923. The valve core 922 is in an I shape and comprises a core rod, and a large disk and a small disk which are positioned at two ends of the core rod. A spring cavity 925 is formed between the end face of the large disc and the valve sleeve 921, a piston cavity 926 is formed between the end face of the small disc and the valve sleeve 921, and a pressure control cavity 927 is formed between the core rod and the inner wall of the valve sleeve 921. The center of the small disc end face is provided with a through hole 928 extending along the core rod to the large disc side face. The through hole 928 is difficult to process and has a large number of manufacturing processes, so that the manufacturing cost is increased, and the oil pump control failure is easily caused by blockage.
Disclosure of Invention
The utility model aims to provide a two-stage variable displacement oil pump control system which can enable a single-acting cavity feedback variable displacement oil pump to realize a two-stage variable displacement function.
The utility model aims to solve the technical problem of providing a pilot valve which is small in size, easy to process and low in manufacturing cost, and when the pilot valve is matched with a switching electromagnetic valve for use, a single-action cavity feedback variable-displacement oil pump can realize a two-stage variable-displacement function.
The embodiment of the utility model provides a control system of a two-stage variable displacement oil pump, which comprises a single-action cavity feedback variable displacement oil pump, an oil outlet of the pump, a main oil duct, an oil pan, a switch electromagnetic valve and a pilot valve, wherein the single-action cavity feedback variable displacement oil pump is connected with the oil outlet of the pump; the single-acting cavity feedback variable displacement oil pump comprises a feedback pressure oil cavity; the pilot valve comprises a valve sleeve, a valve core and a spring; the valve sleeve is provided with a feedback oil passage interface, a main cavity, a first pressure control cavity, a second pressure control cavity and a pressure relief port; the main cavity is respectively communicated with the feedback oil duct interface, the first pressure control cavity, the second pressure control cavity and the pressure relief port; the valve core and the spring are arranged in the main cavity, the spring is abutted against one end of the valve core, a spring cavity is formed between one end of the valve core and the valve sleeve, the first pressure control cavity is close to the other end of the valve core, and the feedback oil duct interface, the second pressure control cavity and the pressure relief opening are respectively arranged on the side face of the main cavity; the feedback oil duct interface is communicated with a feedback pressure oil cavity, the spring cavity and the pressure relief port are respectively communicated with the oil pan, the first pressure control cavity is communicated with the main oil duct or the oil outlet of the pump, and the second pressure control cavity is communicated with the port A of the switch electromagnetic valve; the engine oil flowing into the first pressure control cavity and the second pressure control cavity can generate oil pressure opposite to the direction of spring force applied to the valve core by a spring on the valve core, and the valve core can axially move in the main cavity under the action of the spring force and the oil pressure, so that the feedback oil passage interface is alternatively communicated with the pressure relief port or the first pressure control cavity; the P port of the switch electromagnetic valve is communicated with the main oil duct or the oil outlet of the pump, the T port of the switch electromagnetic valve is communicated with the oil pan, and the A port is communicated with the P port or the T port alternatively along with the switching state switching of the switch electromagnetic valve.
The embodiment of the utility model also provides a pilot valve, which comprises a valve sleeve, a valve core and a spring; the valve sleeve is provided with a feedback oil passage interface, a main cavity, a first pressure control cavity, a second pressure control cavity and a pressure relief port; the main cavity is respectively communicated with the feedback oil duct interface, the first pressure control cavity, the second pressure control cavity and the pressure relief port; the valve core and the spring are arranged in the main cavity, the spring is abutted against one end of the valve core, a spring cavity is formed between one end of the valve core and the valve sleeve, the first pressure control cavity is close to the other end of the valve core, and the feedback oil duct interface, the second pressure control cavity and the pressure relief opening are respectively arranged on the side face of the main cavity; the engine oil flowing into the first pressure control cavity and the second pressure control cavity can generate oil pressure opposite to the direction of spring force applied to the valve core by the spring to the valve core, and the valve core can axially move in the main cavity under the action of the spring force and the oil pressure, so that the feedback oil passage interface is alternatively communicated with the pressure relief port or the first pressure control cavity.
The utility model has at least the following advantages:
1. the two-stage variable displacement oil pump control system of the embodiment enables the valve core to be simultaneously acted by the oil pressure and the spring force of the first pressure control cavity and the second pressure control cavity when the switch electromagnetic valve is in one of the opening state and the closing state, and enables the valve core to be only acted by the oil pressure and the spring force of the first pressure control cavity when the switch electromagnetic valve is in the other of the opening state and the closing state, so that the single-cavity feedback variable displacement oil pump can realize a stable two-stage horizontal control mode;
2. the pilot valve of the embodiment has the advantages of small volume, easy processing and low manufacturing cost.
Drawings
In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the drawings needed to be used in the description of the embodiments will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings based on these drawings without inventive exercise.
Fig. 1 and 2 respectively show two structures of prior pilot valves for enabling a single-acting-chamber feedback variable displacement oil pump to realize a two-stage variable displacement function.
Fig. 3 shows a schematic cross-sectional structure of a pilot valve according to an embodiment of the present invention.
Fig. 4 is a schematic diagram showing the structure of a two-stage variable displacement oil pump control system according to an embodiment of the present invention, in which oil pressure connected to a first pressure chamber of a pilot valve and a P port of a switching solenoid valve is supplied from a main oil gallery.
Fig. 5 is a schematic diagram illustrating a two-stage variable displacement oil pump control system according to an embodiment of the present invention, in which oil pressure connected to a first pressure control chamber of a pilot valve and a P port of an on-off solenoid valve is supplied from a pump oil outlet.
Detailed Description
The utility model is further described below with reference to the accompanying drawings.
Please refer to fig. 3 to 5. The two-stage variable displacement engine oil pump control system comprises a single-acting-cavity feedback variable displacement engine oil pump 1, a check valve 2, an oil outlet 3 of a pump, a safety valve 4, a main oil gallery 5, a pilot valve 6, a switch electromagnetic valve 7 and an oil pan 8.
The single-acting cavity feedback variable displacement oil pump 1 comprises a pump body, a feedback pressure oil cavity 11, a rotor, a variable slider, a return spring and the like.
The check valve 2 is positioned at the oil outlet 3 of the pump to prevent oil from flowing back when the pump stops working.
The safety valve 4 is provided on an oil path between the pump outlet 3 and the oil pan 8, and when the oil pressure of the pump outlet 3 exceeds a set pressure of the safety valve 4, the engine oil of the pump outlet 3 flows into the oil pan 8 through the safety valve 4.
The pilot valve 6 includes a valve sleeve 6a, a valve spool 6b, and a spring 6 c.
The valve sleeve 6a is integrated in the pump body. Valve sleeve 6a is provided with a main chamber 60, a feedback oil passage port 61, a first pressure control chamber 63, a second pressure control chamber 64, and a relief port 65. The main chamber 60 is communicated with the feedback oil passage port 61, the first pressure control chamber 63, the second pressure control chamber 64, and the relief port 65, respectively.
The spool 6b and the spring 6c are disposed in the main chamber 60, the spring 6c abuts one end of the spool 6b, and a spring chamber 62 is formed between one end of the spool 6b and the valve housing 6 a. The first pressure control chamber 63 is located next to the other end of the spool 6b, and the feedback oil passage port 61, the second pressure control chamber 64, and the relief port 65 are provided on the side surface of the main chamber 60, respectively. The feedback oil passage interface 61 is communicated with the feedback pressure oil chamber 11, the spring chamber 62 and the pressure relief port 65 are respectively communicated with the oil pan 8, the first pressure control chamber 63 is always communicated with the main oil passage 5 or the pump oil outlet 3, and the second pressure control chamber 64 is communicated with the port A of the on-off solenoid valve 7. The oil flowing into the first pressure control chamber 63 and the second pressure control chamber 64 generates oil pressure on the spool 6b in a direction opposite to the spring force applied to the spool 6b by the spring 6c, and the spool 6b is axially movable in the main chamber 60 by the spring force and the oil pressure, so that the feedback oil passage port 61 is communicated with the relief port 65 or the first pressure control chamber 63 alternatively.
The P port 71 of the on-off solenoid valve 7 communicates with the main gallery 5 or the pump-out oil port 3, the T port 73 of the on-off solenoid valve 7 communicates with the oil pan 8, and the a port 72 communicates alternatively with the P port 71 or the T port 73 depending on the on-off state of the on-off solenoid valve.
In the present embodiment, the side surface of the valve body 6b is provided with a land 66 having a land surface facing the other end of the valve body 6b, and the land 66 receives oil pressure generated by oil from the second pressure control chamber 64 in a direction opposite to the spring force applied to the valve body 6b by the spring 6 c.
When the system is in a low-pressure stage, the on-off solenoid valve 7 is in an electrified opening state under the control of the ECU, the port P71 is communicated with the port a 72, the port a 72 is not communicated with the port T73, and the pressure oil in the main oil gallery 5 (or the oil outlet 3 of the pump) sequentially passes through the port P71 and the port a 72 of the on-off solenoid valve 7 and enters the second pressure control cavity 64. At this time, the first pressure control chamber 63 and the second pressure control chamber 64 are both communicated with the main gallery 5 (or the pump outlet port 3). That is, the spool 6b is simultaneously acted upon by the oil pressure of the first pressure control chamber 63 and the second pressure control chamber 64 and the spring force.
Before the system pressure (i.e. the engine oil pressure of the main oil gallery or the oil outlet of the pump) reaches a low pressure level (i.e. a set low pressure variable point), the feedback oil gallery interface 61 is communicated with the pressure relief port 65, that is, the feedback pressure oil chamber 11 is communicated with the oil pan 8 through the feedback oil gallery interface 61 and the pressure relief port 65 in sequence. At this point, the variable displacement mechanism is at maximum displacement, and as the speed of rotation increases, the pressure increases until a low pressure level is reached. In the present embodiment, the side surface of the valve spool 6b is provided with an annular groove 67, and the feedback oil passage port 61 communicates with the relief port 65 through a space between the annular groove 67 and the inner wall of the main chamber 60.
When the system pressure reaches a low pressure level, the valve core 6b overcomes the spring force of the spring 6c under the oil pressure action of the first pressure control chamber 63 and the second pressure control chamber 64, moves towards the spring chamber 62, the feedback oil passage port 61 is disconnected from the pressure relief port 65, and is communicated with the first pressure control chamber 63, that is, the feedback pressure oil chamber 11 is communicated with the first pressure control chamber 63 through the feedback oil passage port 61, and the engine oil in the main oil passage 5 or the pump oil outlet 3 enters the feedback pressure oil chamber 11 through the first pressure control chamber 63. The variable mechanism reduces the eccentric amount of the variable slide block and the rotor under the action of the oil pressure of the feedback pressure oil cavity 11, thereby reducing the displacement and the pressure.
Once the pressure is reduced, the spool 6b moves away from the spring chamber 62 under the spring force against the oil pressure in the first and second pressure control chambers 63 and 64, and the feedback oil passage port 61 communicates with the relief port 65 and is disconnected from the first pressure control chamber 63. Namely, the feedback pressure oil chamber 11 is communicated with the oil pan 8 through the feedback oil passage interface 61 and the pressure relief port 65 in sequence. The oil pressure of the feedback pressure oil cavity 11 is rapidly reduced, the displacement of the variable mechanism is increased under the action of the variable spring, and the pressure is increased.
Then, the above two steps are alternately performed, and the system pressure is maintained at a low pressure level.
When the on-off electromagnetic valve 7 is closed under the control of ECU, the system is switched to the high-pressure stage. At this time, the port P71 of the on-off solenoid valve is disconnected from the port a 72, the port a 72 communicates with the port T73, the second pressure control chamber 64 communicates with the oil pan 8 sequentially through the port a 72 and the port T73 of the on-off solenoid valve 7, the oil pressure in the second pressure control chamber 64 is zero, and only the first pressure control chamber 63 communicates with the main oil gallery 5 (or the pump outlet port 3). That is, the spool 6b is acted upon only by the oil pressure and the spring force of the first pressure control chamber 63.
Before the system pressure reaches a high pressure level (i.e., a set high pressure variable point), the feedback oil passage interface 61 is communicated with the pressure relief cavity 65, that is, the feedback pressure oil cavity 11 is communicated with the oil pan 8 sequentially through the feedback oil passage interface 61 and the pressure relief cavity 65. At this time, the displacement of the variable displacement mechanism is increased under the action of the variable displacement spring, and the pressure is rapidly increased to a high-pressure level along with the increase of the rotating speed.
When the pressure reaches the high pressure level, the valve core 6b overcomes the spring force of the spring 6c under the action of the oil pressure of the first pressure control cavity 63, moves towards the spring cavity 62, the feedback oil channel interface 61 is disconnected from the pressure relief opening 65, and is communicated with the first pressure control cavity 63, namely, the feedback pressure oil cavity 11 is communicated with the first pressure control cavity 63 through the feedback oil channel interface 61, and the engine oil of the main oil channel 5 or the pump oil outlet 3 enters the feedback pressure oil cavity 11 through the first pressure control cavity 63. The variable mechanism reduces the eccentric amount of the variable slide block and the rotor under the action of the oil pressure of the feedback pressure oil cavity 11, thereby reducing the displacement and the pressure.
Once the pressure is reduced, the spool 6b is moved away from the spring chamber 62 by the spring force against the oil pressure of the first pressure control chamber 63, and the feedback oil passage port 61 is communicated with the relief port 65 and is disconnected from the first pressure control chamber 63. Namely, the feedback pressure oil chamber 11 is communicated with the oil pan 8 through the feedback oil passage interface 61 and the pressure relief port 65 in sequence. The oil pressure of the feedback pressure oil cavity 11 is rapidly reduced, the displacement of the variable mechanism is increased under the action of the variable spring, and the pressure is increased.
Then, the above two steps are alternately performed, and the system pressure is maintained at a high pressure level.
In the present embodiment, the single-acting-chamber feedback variable displacement oil pump 1 may adopt a vane pump, a rotor pump, a gear pump or the like. Fig. 4 and 5 schematically show the variable mechanism 1a of the single-acting-chamber feedback variable displacement oil pump 1, the oil inlet 12 and the oil outlet 13 of the variable mechanism 1a, and further show the engine 901, the strainer 902, the cooler 93 and the filter 94. Since the cooler 93, the filter 94, and the like are provided between the main gallery 5 and the pump-out port 3, the oil pressure is different between the communication between the first pressure control chamber 63 of the pilot valve 6 and the P port 71 of the on-off solenoid valve 7 with the main gallery 5 than with the pump-out port 3.
Compared with the structure of the pilot valve 92 shown in fig. 2, the valve core 6b of the present embodiment is not provided with a through hole, but the communication between the first pressure control chamber 63 and the feedback pressure oil chamber 11 is realized by arranging the feedback oil passage interface 61 on the valve sleeve 6a, so that the manufacturing process is easier, the manufacturing cost is lower, and the phenomenon of oil pump control failure caused by oil hole blockage is reduced.
Compared with the structure of the pilot valve 91 shown in fig. 1, in the same high and low pressure control mode, assuming that the spool outer diameter at the second pressure control chamber 917 in fig. 1 is the same as the spool outer diameter at the second pressure control chamber 64 in fig. 3, i.e., h1= h3, the spool outer diameter at the first pressure control chamber 916 in fig. 1 is larger than the spool outer diameter at the first pressure control chamber 63 in fig. 3, i.e., h4 > h 2. That is, for the pilot valve structure, the outer diameter of the first pressure control chamber of the pilot valve of the present embodiment can be made smaller, and the structure is more compact. More specifically, in the low-pressure mode (the switch solenoid valve is open), the first pressure control chamber 916 and the second pressure control chamber 917 in fig. 1 are simultaneously filled with oil, and the spool is stressed by a force F2 is low=pIs low in*（πh12/4), in fig. 3, the first pressure control cavity 63 and the second pressure control cavity 64 are simultaneously communicated with oil, and the valve core is stressed by a force F3 is low=pIs low in*（πh32/4），pIs low inThe ECU is adjusted to a low pressure according to the engine fed back by working conditions such as rotating speed, torque load, oil temperature, oil duct pressure and the like; in the high-pressure mode (switch solenoid off), only the second pressure control chamber 917 in FIG. 1 is filled with oil, and the valve core is stressed by F2 high=pHeight of*（π（h12 –h42) 4), in fig. 3, only the first pressure control cavity 63 is filled with oil, and the valve core is stressed by F3 high=pHeight of*（πh22/4），pHeight ofThe ECU feeds back the high pressure required to be adjusted by the engine according to working conditions such as rotating speed, torque load, oil temperature, oil passage pressure and the like. Due to the high-low pressure mode, the valve core moves at the same position, namely the valve core is stressed at the same force. So there is F2 is low=F2 high=F3 is low=F3 high. The formula is summarized as follows, and is derived from the formula: h2 < h4 when h1= h3,namely, the valve core of the embodiment has a compact structure.
h1= h3 formula (1)
F2 is low=pIs low in*（πh12/4) formula (2)
F3 is low=pIs low in*（πh32/4) formula (3)
F2 high=pHeight of*（π（h12 –h42) /4) formula (4)
F3 high=pHeight of*（πh22/4) formula (5)
F2 is low=F2 highFormula (6)
F3 is low=F3 highFormula (7)
2*pIs low in＜ pHeight ofInequality (8)
Substituting the formulas (2) and (4) into the formula (6) to obtain:
pis low in*h12= pHeight of*（h12 –h42) Formula (9)
Substituting inequality (8) into equation (9) to obtain:
h12 ＜ 2*h42inequality (10)
Substituting the formulas (3) and (5) into the formula (7) to obtain:
pis low in* h32= pHeight of*h22 Formula (11)
Substituting inequality (8) into equation (11) to obtain:
2*h22 ＜ h32 inequality (12)
The formula (1), the inequality (10) and the inequality (12) are as follows:
h2＜h4 。
the second-stage variable displacement engine oil pump control system of the embodiment enables the valve core to be simultaneously acted by the oil pressure and the spring force of the first pressure control cavity and the second pressure control cavity when the switch electromagnetic valve is in one of the opening state and the closing state, and enables the valve core to be only acted by the oil pressure and the spring force of the first pressure control cavity when the switch electromagnetic valve is in the other of the opening state and the closing state, so that the single-cavity feedback variable displacement engine oil pump can realize a stable two-stage horizontal control mode.
It will be apparent to those skilled in the art that various changes and modifications may be made in the present invention without departing from the spirit and scope of the utility model. Thus, if such modifications and variations of the present invention fall within the scope of the claims of the present invention and their equivalents, the present invention is also intended to include such modifications and variations.
Claims (8)
1. A control system of a two-stage variable displacement oil pump comprises a single-acting cavity feedback variable displacement oil pump, an oil outlet of the pump, a main oil duct, an oil pan, a switch electromagnetic valve and a pilot valve; the single-acting cavity feedback variable displacement oil pump comprises a feedback pressure oil cavity; the pilot valve is characterized by comprising a valve sleeve, a valve core and a spring;
the valve sleeve is provided with a feedback oil passage interface, a main cavity, a first pressure control cavity, a second pressure control cavity and a pressure relief port; the main cavity is respectively communicated with the feedback oil passage interface, the first pressure control cavity, the second pressure control cavity and the pressure relief port;
the valve core and the spring are arranged in the main cavity, the spring is abutted against one end of the valve core, a spring cavity is formed between one end of the valve core and the valve sleeve, the first pressure control cavity is close to the other end of the valve core, and the feedback oil passage interface, the second pressure control cavity and the pressure relief port are respectively arranged on the side surface of the main cavity; the feedback oil duct interface is communicated with the feedback pressure oil cavity, the spring cavity and the pressure relief port are respectively communicated with the oil pan, the first pressure control cavity is communicated with the main oil duct or the oil outlet of the pump, and the second pressure control cavity is communicated with the port A of the switch electromagnetic valve; the engine oil flowing into the first pressure control cavity and the second pressure control cavity can generate oil pressure opposite to the direction of spring force applied to the valve core by a spring on the valve core, and the valve core can axially move in the main cavity under the action of the spring force and the oil pressure, so that the feedback oil passage interface is alternatively communicated with the pressure relief opening or the first pressure control cavity;
the P port of the switch electromagnetic valve is communicated with the main oil duct or the oil outlet of the pump, the T port of the switch electromagnetic valve is communicated with the oil pan, and the A port is communicated with the P port or the T port alternatively along with the switching state switching of the switch electromagnetic valve.
2. The two-stage variable displacement oil pump control system of claim 1, wherein an annular groove is formed in a side surface of the valve core, and the feedback oil passage port is communicated with the pressure relief port through a space between the annular groove and the inner wall of the main chamber.
3. The two-stage variable displacement oil pump control system of claim 1, wherein a side surface of the spool is provided with a step facing the other end of the spool, the step being adapted to receive the oil pressure generated by the oil from the second pressure control chamber.
4. The two-stage variable displacement oil pump control system of claim 1, comprising a relief valve disposed in the oil path between the pump outlet and the sump, wherein oil from the pump outlet flows through the relief valve into the sump when the oil pressure at the pump outlet exceeds a set pressure of the relief valve.
5. The two-stage variable displacement oil pump control system of claim 1, wherein switching of the on-off state of the on-off solenoid valve is controlled by an ECU.
6. A pilot valve comprises a valve sleeve, a valve core and a spring; the valve sleeve is provided with a feedback oil passage interface, a main cavity, a first pressure control cavity, a second pressure control cavity and a pressure relief port; the main cavity is respectively communicated with the feedback oil passage interface, the first pressure control cavity, the second pressure control cavity and the pressure relief port;
the valve core and the spring are arranged in the main cavity, the spring is abutted against one end of the valve core, a spring cavity is formed between one end of the valve core and the valve sleeve, the first pressure control cavity is close to the other end of the valve core, and the feedback oil passage interface, the second pressure control cavity and the pressure relief port are respectively arranged on the side surface of the main cavity;
the engine oil flowing into the first pressure control cavity and the second pressure control cavity can generate oil pressure opposite to the direction of spring force applied to the valve core by a spring on the valve core, and the valve core can axially move in the main cavity under the action of the spring force and the oil pressure, so that the feedback oil passage interface is alternatively communicated with the pressure relief opening or the first pressure control cavity.
7. The pilot valve as claimed in claim 6, wherein an annular groove is formed in a side surface of the valve spool, and the feedback oil passage port is communicated with the relief port through a space between the annular groove and an inner wall of the main chamber.
8. The pilot valve as claimed in claim 6, wherein a side surface of the valve spool is provided with a step facing the other end of the valve spool, the step being adapted to receive the oil pressure generated by the oil from the second pressure control chamber.
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| CN202122166410.1U CN215804761U (en) | 2021-09-08 | 2021-09-08 | Pilot valve and two-stage variable displacement engine oil pump control system thereof |
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| CN202122166410.1U CN215804761U (en) | 2021-09-08 | 2021-09-08 | Pilot valve and two-stage variable displacement engine oil pump control system thereof |
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