CN106870173B - Engine shutdown phase control mechanism - Google Patents
Engine shutdown phase control mechanism Download PDFInfo
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- CN106870173B CN106870173B CN201710235304.XA CN201710235304A CN106870173B CN 106870173 B CN106870173 B CN 106870173B CN 201710235304 A CN201710235304 A CN 201710235304A CN 106870173 B CN106870173 B CN 106870173B
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- oil duct
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- annular groove
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D17/00—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling
- F02D17/04—Controlling engines by cutting out individual cylinders; Rendering engines inoperative or idling rendering engines inoperative or idling, e.g. caused by abnormal conditions
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N19/00—Starting aids for combustion engines, not otherwise provided for
- F02N19/005—Aiding engine start by starting from a predetermined position, e.g. pre-positioning or reverse rotation
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N19/00—Starting aids for combustion engines, not otherwise provided for
- F02N19/005—Aiding engine start by starting from a predetermined position, e.g. pre-positioning or reverse rotation
- F02N2019/008—Aiding engine start by starting from a predetermined position, e.g. pre-positioning or reverse rotation the engine being stopped in a particular position
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Gripping On Spindles (AREA)
Abstract
When the engine stop phase control mechanism starts to work, a hydraulic cylinder assembly on a fixed shaft rotates along with a main gear fixed on a crankshaft, and an electromagnetic chuck starts to be electrified to enable an electromagnetic chuck II to move, so that a friction plate fixed on the electromagnetic chuck II is contacted with a friction plate fixed on the electromagnetic chuck I, and the crankshaft starts to be primarily decelerated; meanwhile, a piston in the secondary telescopic hydraulic cylinder stretches out and contacts with a phase control component in the phase control disc, and at the moment, the crankshaft starts to perform secondary deceleration and phase fixing is performed; the invention can directly act on the crankshaft, can realize two-stage deceleration of the crankshaft, can realize reliable control of the stop phase, and can ensure that the piston is in a phase capable of successfully realizing starting when the engine is directly started each time so as to ensure the success rate of starting the engine.
Description
Technical Field
The invention belongs to the technical field of engines, and particularly relates to an engine stop phase control mechanism.
Background
With the increasing exhaustion of petroleum resources and the increasing serious environmental pollution, people put higher and higher requirements on the traditional vehicle power, especially in the aspect of energy conservation, so the development of the energy-saving technology of the internal combustion engine is particularly important. An automatic start-stop system is a technology capable of enabling an automobile engine to start and stop flexibly, and has greatly helped to save energy of a gasoline engine, so that attention has been paid to the automatic start-stop system. The automatic start-stop system has various realization modes, one of the automatic start-stop system is in a direct start mode, and the start mode does not need a starter, so that the cost of an automobile can be greatly reduced, and meanwhile, the start noise can be reduced, so that the automatic start-stop system has good application and popularization prospects on a GDI engine. However, the direct start mode has a certain requirement on the initial phase of the piston during start, if the phase of the piston after stopping is not in the stopping range, the function of the automatic start-stop system cannot be achieved, and therefore the phase control of the piston after stopping is very important.
Disclosure of Invention
For the problems in the prior art existing at present, the invention provides a novel engine shutdown phase control mechanism which can directly act on a crankshaft to realize reliable control of a shutdown phase range, and finally, the purposes of shutdown deceleration and shutdown phase control are achieved.
In order to achieve the above purpose, the invention adopts the following technical scheme:
the engine stop phase control mechanism is characterized by comprising a hydraulic cylinder assembly I, a phase control disc assembly II, a fixed shaft, a main gear and a crankshaft, and is characterized in that:
the hydraulic cylinder assembly I is arranged on the fixed shaft, clearance fit exists between the hydraulic cylinder assembly I and the fixed shaft, the end face of the friction disc assembly II is fixedly connected to the surface of the cylinder body, one end of the fixed shaft penetrates through the friction disc assembly II to be fixed in the cylinder body, the main gear is arranged on the crankshaft, and the main gear is connected with the crankshaft through a key and is kept in a meshed state with the hydraulic cylinder gear.
The hydraulic cylinder assembly I consists of a primary spring A1, a hydraulic cylinder gear body 2, a primary piston A base 3, a primary piston A4, a secondary piston A5, an oil inlet hole A6, a secondary spring A7, a hydraulic cylinder gear cover 8, a primary spring B9, a primary piston B base 10, a secondary spring B11, an oil inlet hole B12, a secondary piston B13, a primary piston B14, an electromagnetic chuck I17, a friction plate A18, an oil duct IA 42, an oil duct IIA 43, an annular oil duct I36, an oil duct IB 39, an oil duct IIB 40 and a shaft hole 41; the hydraulic cylinder gear body 2 is provided with a hydraulic cavity A34 and a hydraulic cavity B37; the primary piston A4 and the primary piston B14 are respectively arranged in a hydraulic cavity A34 and a hydraulic cavity B37 of the hydraulic cylinder gear body 2 and are in clearance fit with the cavity wall; the secondary piston A5 and the secondary piston B13 are respectively arranged in the primary piston A4 and the primary piston B14 and are in clearance fit with the cavity wall; the primary spring A1 and the primary spring B9 are respectively arranged in the hydraulic cavity A34 and the hydraulic cavity B37, one end of the primary spring A1 and one end of the primary spring B9 are respectively connected with shoulders of the primary piston A4 and the primary piston B14, and the other end of the primary spring A1 and the other end of the primary spring B9 are respectively connected with bottom ends of the hydraulic cavity A34 and the hydraulic cavity B37; the secondary springs A7 and B11 are respectively arranged in the primary pistons A4 and B14, one ends of the secondary springs A7 and B11 are respectively connected with the shoulders of the secondary pistons A5 and B13, and the other ends of the secondary springs A and B are respectively connected with the primary piston A base 3 and the primary piston B base 10; the base 3 of the primary piston A and the base 10 of the primary piston B are respectively connected with the primary piston A4 and the primary piston B14 through threads, the centers of the base 3 of the primary piston A and the base 10 of the primary piston B are respectively provided with a through hole A64 and a through hole B64, and the bottoms of the secondary piston A5 and the secondary piston B13 can freely slide in the through holes; a limiting hole A35 and a limiting hole B38 are formed in the hydraulic cylinder gear body 2, the central lines of the limiting hole A35 and the limiting hole B38 are respectively overlapped with the piston rod axes of the secondary piston A5 and the secondary piston B13, and the piston rods of the secondary piston A5 and the secondary piston B13 are in clearance fit with the limiting hole A35 and the limiting hole B38; the hydraulic cylinder gear body 2 is internally provided with an oil duct IA 42, an oil duct IIA 43, an annular oil duct I36, an oil duct IB 39, an oil duct IIB 40 and a shaft hole 41, a hydraulic cavity A34 is communicated with the oil duct IIA 43 through the annular oil duct I36, the oil duct IA 42 and the oil duct IIB 40, and a hydraulic cavity B37 is communicated with the oil duct IIB 40 through the annular oil duct I36; the hydraulic cylinder gear cover 8 is connected with the hydraulic cylinder gear body 2 through threads, the electromagnetic chuck I17 is fixedly connected to the end face of the hydraulic cylinder gear body 2, and the friction plate A18 is fixedly connected to the upper portion of the electromagnetic chuck I17.
The phase control disc assembly II consists of a friction plate B19, an electromagnetic chuck II 20, a rubber pad 21, a connecting rod A22, a connecting rod B28, a return spring A23, a return spring B29, a phase control disc 26, a cavity A25, a cavity B31, a support plate A48, a support plate B55, an oil duct IIIA 47, an oil duct IVA 51, an oil duct IIIB 58, an oil duct IVB 60 and an annular oil duct II 49; the phase control disc 26 is internally provided with an annular groove A45 and an annular groove B54, the annular groove A45 and the annular groove B54 are respectively provided with a buffer piston A46 and a buffer piston B57, and the buffer piston A46 and the buffer piston B57 are in clearance fit with the annular groove A45 and the annular groove B54; one end of the arc-shaped spring A50 and one end of the arc-shaped spring B56 are respectively fixedly connected with a supporting plate A48 on the buffer piston A46 and a supporting plate B55 on the buffer piston B57, and the other end of the arc-shaped spring A50 and the other end of the arc-shaped spring B56 are respectively connected with the bottom ends of the annular groove A45 and the annular groove B54; the buffer rubber A44 and the buffer rubber B53 are respectively arranged at the top ends of the annular groove A45 and the annular groove B54, and the top ends of the buffer piston A46 and the buffer piston B57; the pressure limiting valve A52 and the pressure limiting valve B59 are respectively arranged at the bottom ends of the annular groove A45 and the annular groove B54; the phase control disc 26 is internally provided with an oil duct IIIA 47, an oil duct IVA 51, an oil duct IIIB 58, an oil duct IVB 60 and an annular oil duct II 49; the annular grooves A45, the annular grooves B54 and the annular oil duct II 49 are communicated through an oil duct IIIA 47 and an oil duct IIIB 58 respectively; the oil outlets of the pressure limiting valve A52 and the pressure limiting valve B59 are communicated with the annular oil duct II 49 through an oil duct IVA 51 and an oil duct IVB 60 respectively; the connecting rod A22 and the connecting rod B28 are fixedly connected with the electromagnetic chuck II 20 through threads, and the return spring A23 and the return spring B29 are respectively arranged in the cavity A25 and the cavity B31 of the cylinder 33 and respectively contacted with the baffle A24 and the baffle B30 on the connecting rod A22 and the connecting rod B28; rubber pad 21 is fixed on the surface of phase control plate 26, and friction disc B19 is fixed on the surface of electromagnetic chuck II 20.
The fixed shaft 27 is internally provided with an oil duct V61, a main oil duct 62 and an oil duct VI 63; wherein, the main oil duct 62, the oil duct V61, the annular oil duct I36, the oil duct IIA 43 and the oil duct IA 42 are communicated with each other; the main oil duct 62, the oil duct V61, the annular oil duct I36, the oil duct IIB 40 and the oil duct IB 39 are communicated with each other; the main oil duct 62, the oil duct VI 63, the annular oil duct II 49 and the oil duct IIIA 47 are communicated with each other; the main oil duct 62, the oil duct VI 63, the annular oil duct II 49 and the oil duct IIIB 58 are communicated with each other. The invention can directly act on the crankshaft, realize the reliable control of the stop phase range, ensure that the engine piston is in a phase capable of successfully realizing the starting when directly starting each time, and ensure the success rate of the starting of the engine.
The working process of the device is as follows:
when the engine is in a working state, two stages of pistons in the hydraulic cylinder are all in an initial position, wherein the primary spring A1 and the primary spring B9 are in a compressed state, the secondary spring A7 and the secondary spring B11 are in a free telescopic state, hydraulic oil in the main oil duct 62 is not provided with oil pressure, the electromagnetic chuck I17 is not electrified, the electromagnetic chuck I17 and the electromagnetic chuck II 20 are in a separated state, the hydraulic cylinder assembly I idles along with the main gear 16 along with the fixed shaft 27, and the phase control disc assembly II is fixed on the cylinder body 33 and does not rotate.
If the GDI engine is to adopt the direct start mode, after a specific decision rule is satisfied in the shutdown process, the control system controls the solenoid valve outside the main oil duct 62 to be quickly opened, increases the hydraulic oil pressure of hydraulic oil in the main oil duct 62, and makes the hydraulic oil enter the oil duct ia 42, the oil duct ia 43, the oil duct ib 39 and the oil duct ib 40 through the oil duct v 61 and the annular oil duct i 36 respectively, and finally enter the hydraulic cavity a34 and the hydraulic cavity B37; the high-pressure hydraulic oil enters the hydraulic cavity A34 and the hydraulic cavity B37 and then acts on the primary piston A4 and the primary piston B14 respectively to compress the secondary spring A7 and the secondary spring B11, when the secondary spring A7 and the secondary spring B11 are compressed to a certain extent, the hydraulic oil pressure is larger than the initial pretightening force of the primary spring A1 and the primary spring B9, the hydraulic oil starts to compress the secondary piston A5 and the secondary piston B13, the secondary piston A5 and the secondary piston B13 move to start to compress the primary spring A1 and the primary spring B9, meanwhile, the electromagnetic chuck I17 starts to be electrified to move the electromagnetic chuck II 20, and then the baffle A24 and the baffle B30 on the connecting rod A22 and the connecting rod B28 compress the return spring A23 and the return spring B29, so that the friction plate A18 and the friction plate B19 fixed on the electromagnetic chuck I17 and the electromagnetic chuck II 20 start to contact, and thus friction force is generated, and the crankshaft 32 starts to perform primary deceleration; during the deceleration of the crankshaft 32, when the rotational speed of the crankshaft 32 decreases to a predetermined value, the piston rods of the secondary piston A5 and the secondary piston B13 enter the annular groove a45 and the annular groove B54 inside the phase control disc 26, respectively, and at a lower rotational speed of the crankshaft, the piston rods of the secondary piston A5 and the secondary piston B13 start to contact the buffer rubber a44 and the buffer rubber B53 at the tops of the buffer piston a46 and the buffer piston B57, respectively, and at the same time the buffer piston a46 and the buffer piston B57 start to compress the arc spring a50 and the arc spring B56, respectively; when the buffer piston a46 and the buffer piston B57 just move to a fixed position in the process of compressing the arc springs a50 and B56, the oil passage openings of the oil passages iii a47 and iii B58 are blocked by the buffer piston a46 and B57 respectively, high-pressure oil entering the oil passages iii a47 and iii B58 respectively through the main oil passage 62, the oil passage vi 63 and the annular oil passage ii 49 stops entering the annular groove a45 and the annular groove B54, the buffer piston a46 and the buffer piston B57 compress hydraulic oil entering the annular groove a45 and the annular groove B54 in the moving process, so that the buffer piston a46 and the buffer piston B57 play a role of reducing and buffering, the rotating speed of the crankshaft 32 is further reduced until stopping, and the pressure limiting valve a52 and the pressure limiting valve B59 are opened and depressurized when the hydraulic oil pressure inside the annular groove a45 and the annular groove B54 reaches a certain limit value, so that the purpose of controlling the shutdown phase is achieved while the two-stage deceleration of the crankshaft is achieved.
When the crankshaft stops rotating, in order not to influence the next starting process, piston rods of the secondary piston A5 and the secondary piston B13 need to be withdrawn from the annular groove A45 and the annular groove B54, at the moment, the electromagnetic chuck I17 is powered off, the electromagnetic chuck II 20 returns under the action of the return spring A23 and the return spring B29, the friction plate A18 and the friction plate B19 are separated, a rubber pad 21 fixed on the phase control plate 26 can prevent the electromagnetic chuck II 20 from violently colliding with the phase control plate 26 in the returning process, a pressure relief valve connected with the outside of the main oil duct 62 is opened, and the pressure of high-pressure hydraulic oil in the main oil duct 62 is gradually reduced; when the pressure is reduced to an initial value, an externally connected electromagnetic valve is opened, the primary piston A4 and the primary piston B14 return to the original states under the action of the restoring force of the primary spring A1 and the primary spring B9, the bottoms of the secondary piston A5 and the secondary piston B13 retract from the annular groove A45 and the annular groove B54 respectively, the pressure limiting valve A52 and the pressure limiting valve B59 are opened, and hydraulic oil in the annular groove A45 and the annular groove B54 flows back through the oil duct IVA 51 and the oil duct IVB 60 respectively, the annular oil duct II 49, the oil duct VI 63 and the main oil duct 62, so that one working cycle is completed.
Drawings
FIG. 1 is a schematic diagram of a novel engine shutdown phase control mechanism
Fig. 2 is a front view of the cylinder gear body 2 in the cylinder assembly
FIG. 3 is a B-B side view of the cylinder gear 2 in the cylinder assembly
FIG. 4 is an A-A side view of the cylinder gear 2 in the cylinder assembly
Fig. 5 is a schematic diagram of the phase control disk 26
FIG. 6 is a D-D view of the phase control disk 26
FIG. 7 is an E-E view of the phase control disk 26
Fig. 8 is a schematic structural view of the fixed shaft 27
FIG. 9 is a F-F side view of the stationary shaft 27
FIG. 10 is a schematic view of the structure of the primary piston base
FIG. 11 is a G-G view of the primary piston base
Wherein: a hydraulic cylinder assembly II, a phase control disc assembly 1, a primary spring A2, a hydraulic cylinder gear body 3, a primary piston A base 4, a primary piston A5, a secondary piston A6, an oil inlet hole A7, a secondary spring A8, a hydraulic cylinder gear cover 9, a primary spring B10, a primary piston B base 11, a secondary spring B12, an oil inlet hole B13, a secondary piston B14, a primary piston B15, a key 16, a main gear 17, an electromagnetic chuck I18, a friction plate A19, a friction plate B20, an electromagnetic chuck II 21, a rubber gasket 22, a connecting rod A23, a return spring A24, a baffle A25, a cavity A26, a phase control disc 27, a fixed shaft 28, a connecting rod B29, a return spring B. 30, baffle B31, cavity B32, crankshaft 33, cylinder 34, hydraulic chamber A35, limiting bore A36, annular oil gallery I37, hydraulic chamber B38, limiting bore B39, oil gallery IB 40, oil gallery IIB 41, shaft bore 42, oil gallery IA 43, oil gallery IIA 44, cushion rubber A45, annular groove A46, cushion piston A47, oil gallery IIIA 48, support plate A49, annular oil gallery II 50, arc spring A51, oil gallery IVA 52, pressure limiting valve A53, cushion rubber B54, annular groove B55, support plate B56, arc spring B57, cushion piston B58, oil gallery IIIB 59, pressure limiting valve B60, oil gallery IVB 61, oil gallery V62, main oil gallery 63, oil gallery VI 64
Detailed Description
The following describes the shape and structure of each mechanism, the mutual position and connection relation between each part, the action and working principle of each part, etc. according to the specific embodiment of the present invention in further detail:
referring to fig. 1, the engine stop phase control mechanism mainly comprises a hydraulic cylinder assembly i, a phase control disc assembly ii, a fixed shaft 27, a main gear 16 and a crankshaft 32: the hydraulic cylinder assembly I is arranged on the fixed shaft 27 and is in clearance fit with the fixed shaft 27, so that the hydraulic cylinder assembly I can freely rotate on the fixed shaft 26; the phase control disc assembly II is fixedly connected to the surface of the cylinder 33; one end of the fixed shaft 27 passes through the centers of the hydraulic cylinder component I and the phase control disc component II, is in clearance fit, and the other end of the fixed shaft is fixedly connected in the cylinder body 33; the main gear 16 is mounted on the crankshaft 32, is connected to the crankshaft 32 by the key 15, and is held in engagement with the cylinder gear body 2 of the cylinder assembly i.
The hydraulic cylinder assembly I consists of a primary spring A1, a hydraulic cylinder gear body 2, a primary piston A base 3, a primary piston A4, a secondary piston A5, an oil inlet hole A6, a secondary spring A7, a hydraulic cylinder gear cover 8, a primary spring B9, a primary piston B base 10, a secondary spring B11, an oil inlet hole B12, a secondary piston B13, a primary piston B14, an electromagnetic chuck I17, a friction plate A18, an oil duct IA 42, an oil duct IIA 43, an annular oil duct I36, an oil duct IB 39, an oil duct IIB 40 and a shaft hole 41.
The hydraulic cylinder gear body 2 is provided with a hydraulic cavity A34 and a hydraulic cavity B37, and is arranged in a symmetrical shaft hole 41.
The primary piston A4 and the primary piston B14 are respectively arranged in a hydraulic cavity A34 and a hydraulic cavity B37 of the hydraulic cylinder gear body 2 and are in clearance fit with the cavity wall; the secondary piston A5 and the secondary piston B13 are respectively arranged in the primary piston A4 and the primary piston B14, and the inner walls of the primary piston A4 and the primary piston B14 are in clearance fit. The primary piston A4 and the secondary piston A5 and the primary piston B14 and the secondary piston B13 respectively form two-stage telescopic pistons, so that the response speed is higher.
The primary springs A1 and B9 are respectively arranged in the hydraulic cavity A34 and B37, one end of the primary springs A1 and B9 is respectively connected with the shoulders of the primary pistons A4 and B14, and the other end of the primary springs A1 and B9 is respectively connected with the bottoms of the hydraulic cavity A34 and B37; the secondary springs A7 and B11 are respectively arranged in the primary pistons A4 and B14, one ends of the secondary springs A7 and B11 are respectively connected with the shoulders of the secondary pistons A5 and B13, and the other ends of the secondary springs A and B are respectively connected with the primary piston A base 3 and the primary piston B base 10; the primary piston A4 and the primary piston B14, the secondary piston A5 and the secondary piston B13 can return under the action of no hydraulic oil, the secondary spring A7 and the secondary spring B11 are in a pre-tightening state, and the primary spring A1 and the primary spring B9 are in a free state.
The primary piston A base 3 and the primary piston B base 10 are respectively connected with the primary piston A4 and the primary piston B14 through threads, the centers of the primary piston A base 3 and the primary piston B base 10 are respectively provided with a through hole A64 and a through hole B64, the bottoms of the secondary piston A5 and the secondary piston B13 can freely slide in the through holes, and simultaneously, the support and fixation effects on the secondary piston A5 and the secondary piston B13 can be achieved.
The hydraulic cylinder gear body 2 is internally provided with an oil duct IA 42, an oil duct IIA 43, an annular oil duct I36, an oil duct IB 39, an oil duct IIB 40 and a shaft hole 41, a hydraulic cavity A34 is communicated with the oil duct IIA 43 through the annular oil duct I36, the oil duct IA 42 and the oil duct IIB 40, and a hydraulic cavity B37 is communicated with the oil duct IIB 40 through the annular oil duct I36. The annular oil duct I36 can ensure that the oil duct V61 on the fixed shaft 26 and the annular oil duct I36 are kept in a communicated state during the rotation of the hydraulic cylinder gear body 2 due to the rotation of the hydraulic cylinder gear body 2.
The hydraulic cylinder gear cover 8 is connected with the hydraulic cylinder gear body 2 through threads, so that the internal parts are convenient to mount and dismount; the electromagnetic chuck I17 is fixedly connected to the end face of the hydraulic cylinder gear body 2, and the friction plate A18 is fixedly connected to the electromagnetic chuck I17.
Referring to fig. 2, 3 and 4, the hydraulic cylinder gear body 2 is internally provided with a hydraulic cavity a34, a hydraulic cavity B37, a limiting hole a35 and a limiting hole B38.
A limiting hole A35 and a limiting hole B38 are formed in the hydraulic cylinder gear body 2, the central lines of the limiting hole A35 and the limiting hole B38 are respectively overlapped with the axial lines of piston rods of the secondary piston A5 and the secondary piston B13, and the piston rods of the secondary piston A5 and the secondary piston B13 are in clearance fit with the limiting hole A35 and the limiting hole B38; the limiting hole can play a role in fixing and supporting, and the secondary piston A5 and the secondary piston B13 are prevented from being offset under the action of external force after extending out.
Referring to fig. 5, 6 and 7, the phase control disc assembly ii is composed of a friction plate B19, an electromagnetic chuck ii 20, a rubber pad 21, a connecting rod a22, a connecting rod B28, a return spring a23, a return spring B29, a phase control disc 26, a cavity a25, a cavity B31, a support plate a48, a support plate B55, an oil passage iii a47, an oil passage iv a51, an oil passage iii B58, an oil passage iv B60 and an annular oil passage ii 49.
The phase control disk 26 is internally provided with an annular groove A45 and an annular groove B54 which are symmetrically distributed.
The buffer piston A46 and the buffer piston B57 are respectively arranged in the annular groove A45 and the annular groove B54, and clearance fit exists between the buffer piston A46 and the buffer piston B57 and between the buffer piston A45 and the annular groove B54.
The arc spring A50 and the arc spring B56 are respectively fixed on the supporting plate A48 on the buffer piston A46 and the supporting plate B55 on the buffer piston B57 at one end, and are respectively connected with the bottom ends of the annular groove A45 and the annular groove B54 at the other end, so that the buffer effect can be achieved, and the buffer piston A46 and the buffer piston B57 can be guaranteed to automatically reset under the action of no external force.
The buffer rubber A44 and the buffer rubber B53 are respectively arranged at the top ends of the annular groove A45 and the annular groove B54 and the top ends of the buffer piston A46 and the buffer piston B57, so that the secondary piston A5 and the secondary piston B13 can be prevented from violently colliding with the wall surfaces of the annular groove A45 and the annular groove B54 to play a role in buffering when entering the annular groove A45 and the annular groove B54.
The phase control disc 26 is internally provided with an oil duct IIIA 47, an oil duct IVA 51, an oil duct IIIB 58, an oil duct IVB 60 and an annular oil duct II 49, wherein the annular groove A49, the annular groove B54 and the annular oil duct II 49 are respectively communicated with each other through the oil duct IIIA 47 and the oil duct IIIB 58.
The oil outlets of the pressure limiting valve A52 and the pressure limiting valve B59 are communicated with the annular oil duct II 49 through the oil duct IVA 51 and the oil duct IVB 60 respectively, and the pressure limiting valve A52 and the pressure limiting valve B59 mainly prevent the oil pressure in the annular groove A45 and the annular groove B54 from being overlarge so as to realize the pressure relief effect.
The rubber pad 21 is fixed on the surface of the phase control disc 26, so that the electromagnetic chuck II 20 can be prevented from being in severe collision with the surface of the phase control disc 26 in the returning process to play a certain role in buffering.
The friction plate B19 is fixed on the surface of the electromagnetic chuck II 20, the connecting rod A22 and the connecting rod B28 are connected with the electromagnetic chuck II 20 through threads, the return spring A23 and the return spring B29 are respectively arranged in the cavity A25 and the cavity B31 in the cylinder 33 and respectively contact with the baffle A24 and the baffle B30 on the connecting rod A22 and the connecting rod B28, and therefore the buffer piston A46 and the buffer piston B57 can automatically reset under the action of no external force.
Referring to fig. 8 and 9, the fixed shaft 27 is internally provided with an oil passage v 61, a main oil passage 62 and an oil passage vi 63; wherein, the main oil duct 62, the oil duct V61, the annular oil duct I36, the oil duct IIA 43 and the oil duct IA 42 are communicated with each other; the main oil duct 62, the oil duct V61, the annular oil duct I36, the oil duct IIB 40 and the oil duct IB 39 are communicated with each other; the main oil duct 62, the oil duct VI 63, the annular oil duct II 49 and the oil duct IIIA 47 are communicated with each other; the main oil duct 62, the oil duct VI 63, the annular oil duct II 49 and the oil duct IIIB 58 are communicated with each other.
Referring to fig. 10 and 11, through holes 64 are formed in the base 3 of the primary piston a and the base 10 of the primary piston B, and a clearance fit relationship exists between the through holes and the bottoms of the secondary piston A5 and the secondary piston B13.
The working process of the invention
When the engine is in a working state, two stages of pistons in the hydraulic cylinder are all in an initial position, wherein the primary spring A1 and the primary spring B9 are in a compressed state, the secondary spring A7 and the secondary spring B11 are in a free telescopic state, hydraulic oil in the main oil duct 62 is not provided with oil pressure, the electromagnetic chuck I17 is not electrified, the electromagnetic chuck I17 and the electromagnetic chuck II 20 are in a separated state, the hydraulic cylinder assembly I idles along with the main gear 16 along with the fixed shaft 27, and the phase control disc assembly II is fixed on the cylinder body 33 and does not rotate.
If the GDI engine is to adopt a direct starting mode, after a specific judging principle is met in the stopping process, the control system controls the electromagnetic valve outside the main oil duct 62 to be quickly opened, the oil pressure of hydraulic oil in the main oil duct 62 is increased, and the hydraulic oil respectively enters an oil duct IA 42, an oil duct IIA 43, an oil duct IB 39 and an oil duct IIB 40 through an oil duct V61 and an annular oil duct I36 and finally enters a hydraulic cavity A34 and a hydraulic cavity B37; the high-pressure hydraulic oil enters the hydraulic cavity A34 and the hydraulic cavity B37 and then acts on the primary piston A4 and the primary piston B14 respectively to compress the secondary spring A7 and the secondary spring B11, when the secondary spring A7 and the secondary spring B11 are compressed to a certain degree, the hydraulic oil starts to compress the secondary piston A5 and the secondary piston B13 when the hydraulic oil pressure is larger than the initial pretightening force of the primary spring A1 and the primary spring B9, so that the secondary piston A5 and the secondary piston B13 move to start to compress the primary spring A1 and the primary spring B9; simultaneously, the electromagnetic chuck I17 starts to be electrified, so that the electromagnetic chuck II 20 moves, the baffle A24 and the baffle B30 on the connecting rod A22 and the connecting rod B28 compress the return spring A23 and the return spring B29, the friction plate A18 and the friction plate B19 fixed on the electromagnetic chuck I17 and the electromagnetic chuck II 20 start to contact, friction force is generated, and the crankshaft 32 starts to perform primary deceleration; during the deceleration of the crankshaft 32, when the rotational speed of the crankshaft 32 decreases to a predetermined value, the piston rods of the secondary piston A5 and the secondary piston B13 enter the annular groove a45 and the annular groove B54 inside the phase control disc 26, respectively, and at a lower rotational speed of the crankshaft, the piston rods of the secondary piston A5 and the secondary piston B13 start to contact the buffer rubber a44 and the buffer rubber B53 at the tops of the buffer piston a46 and the buffer piston B57, respectively, and at the same time the buffer piston a46 and the buffer piston B57 start to compress the arc spring a50 and the arc spring B56, respectively; when the buffer piston A46 and the buffer piston B57 just move to a fixed position in the process of compressing the arc-shaped spring A50 and the arc-shaped spring B56, the oil passage openings of the oil passage III A47 and the oil passage III B58 are respectively blocked by the buffer piston A46 and the buffer piston B57, high-pressure oil which respectively enters the oil passage III A47 and the oil passage III B58 through the main oil passage 62, the oil passage VI 63 and the annular oil passage II 49 stops entering the annular groove A45 and the annular groove B54, the buffer piston A46 and the buffer piston B57 compress hydraulic oil which enters the annular groove A45 and the annular groove B54 in the moving process, so that the function of reducing and buffering is achieved, the rotating speed of the crankshaft 32 is further reduced until the crankshaft stops, and the pressure limiting valve A52 and the pressure limiting valve B59 can be opened for reducing the pressure when the hydraulic oil pressure of the hydraulic oil in the annular groove A45 and the annular groove B54 reaches a certain limit value, and the purpose of controlling the shutdown phase is achieved at the same time.
When the crankshaft stops rotating, in order not to influence the next starting process, piston rods of the secondary piston A5 and the secondary piston B13 need to be withdrawn from the annular groove A45 and the annular groove B54, at the moment, the electromagnetic chuck I17 is powered off, the electromagnetic chuck II 20 returns under the action of the return spring A23 and the return spring B29, the friction plate A18 and the friction plate B19 are separated, a rubber pad 21 fixed on the phase control plate 26 can prevent the electromagnetic chuck II 20 from violently colliding with the phase control plate 26 in the returning process, a pressure relief valve connected with the outside of the main oil duct 62 is opened, and the pressure of high-pressure hydraulic oil in the main oil duct 62 is gradually reduced; when the pressure is reduced to an initial value, an externally connected electromagnetic valve is opened, the primary piston A4 and the primary piston B14 return to the original states under the action of the restoring force of the primary spring A1 and the primary spring B9, the bottoms of the secondary piston A5 and the secondary piston B13 retract from the annular groove A45 and the annular groove B54 respectively, the pressure limiting valve A52 and the pressure limiting valve B59 are opened, and hydraulic oil in the annular groove A45 and the annular groove B54 flows back through the oil duct IVA 51 and the oil duct IVB 60 respectively, the annular oil duct II 49, the oil duct VI 63 and the main oil duct 62, so that one working cycle is completed.
Claims (2)
1. The engine stop phase control mechanism is characterized by comprising a hydraulic cylinder assembly (I), a phase control disc assembly (II), a fixed shaft (27), a main gear (16) and a crankshaft (32): the hydraulic cylinder assembly (I) is arranged on the fixed shaft (27) and is in clearance fit with the fixed shaft (27); the phase control disc assembly (II) is fixedly connected to the surface of the cylinder body (33); one end of the fixed shaft (27) passes through the centers of the hydraulic cylinder component (I) and the phase control disc component (II) and is in clearance fit, and the other end of the fixed shaft is fixedly connected in the cylinder body (33); the main gear (16) is arranged on the crankshaft (32), is connected with the crankshaft (32) through a key (15) and is kept meshed with a hydraulic cylinder gear body (2) of a hydraulic cylinder assembly (I), and the hydraulic cylinder assembly (I) consists of a primary spring A (1), a hydraulic cylinder gear body (2), a primary piston A base (3), a primary piston A (4), a secondary piston A (5), an oil inlet hole A (6), a secondary spring A (7), a hydraulic cylinder gear cover (8), a primary spring B (9), a primary piston B base (10), a secondary spring B (11), an oil inlet hole B (12), a secondary piston B (13), a primary piston B (14), an electromagnetic chuck I (17), a friction plate A (18), an oil duct IA (42), an oil duct IIA (43), an annular oil duct I (36), an oil duct IB (39), an oil duct IIB (40) and a shaft hole (41); the hydraulic cylinder gear body (2) is provided with a hydraulic cavity A (34) and a hydraulic cavity B (37); the primary piston A (4) and the primary piston B (14) are respectively arranged in a hydraulic cavity A (34) and a hydraulic cavity B (37) of the hydraulic cylinder gear body (2) and are in clearance fit with the cavity wall; the secondary piston A (5) and the secondary piston B (13) are respectively arranged in the primary piston A (4) and the primary piston B (14) and are in clearance fit with the inner walls of the primary piston A (4) and the primary piston B (14); the primary spring A (1) and the primary spring B (9) are respectively arranged in the hydraulic cavity A (34) and the hydraulic cavity B (37), one end of the primary spring A is respectively connected with the shoulders of the primary piston A (4) and the primary piston B (14), and the other end of the primary spring A is respectively connected with the bottom ends of the hydraulic cavity A (34) and the hydraulic cavity B (37); the secondary spring A (7) and the secondary spring B (11) are respectively arranged in the primary piston A (4) and the primary piston B (14), one end of the secondary spring A is respectively connected with the shoulders of the secondary piston A (5) and the secondary piston B (13), and the other end of the secondary spring A is respectively connected with the base (3) of the primary piston A and the base (10) of the primary piston B; the base (3) of the primary piston A and the base (10) of the primary piston B are respectively connected with the primary piston A (4) and the primary piston B (14) through threads, the centers of the base (3) of the primary piston A and the base (10) of the primary piston B are respectively provided with a through hole A (64) and a through hole B (64), and the bottoms of the secondary piston A (5) and the secondary piston B (13) can freely slide in the through holes A (64) and the through holes B (64); a limiting hole A (35) and a limiting hole B (38) are formed in the hydraulic cylinder gear body (2), the central lines of the limiting hole A (35) and the limiting hole B (38) are respectively overlapped with the piston rod axes of the secondary piston A (5) and the secondary piston B (13), and the piston rods of the secondary piston A (5) and the secondary piston B (13) are in clearance fit with the limiting hole A (35) and the limiting hole B (38); the hydraulic cylinder gear body (2) is internally provided with an oil duct IA (42), an oil duct IIA (43), an annular oil duct I (36), an oil duct IB (39), an oil duct IIB (40) and a shaft hole (41), the hydraulic cavity A (34) is communicated with the oil duct IIA (43) through the annular oil duct I (36), the oil duct IA (42) and the oil duct IIA (36), and the hydraulic cavity B (37) is communicated with the oil duct IB (40) through the annular oil duct I (36), the oil duct IB (39); the hydraulic cylinder gear cover (8) is connected with the hydraulic cylinder gear body (2) through threads, the upper part of the electromagnetic chuck I (17) is fixedly connected to the end face of the hydraulic cylinder gear body (2), the friction plate A (18) is fixedly connected to the upper part of the electromagnetic chuck I (17), the phase control disc assembly (II) consists of a friction plate B (19), an electromagnetic chuck II (20), a rubber pad (21), a connecting rod A (22), a connecting rod B (28), a return spring A (23), a return spring B (29), a phase control disc (26), a cavity A (25), a cavity B (31), a supporting plate A (48), a supporting plate B (55), a pressure limiting valve A (52), a pressure limiting valve B (59), an oil duct IIIA (47), an oil duct IVA (51), an oil duct IIIB (58), an oil duct IVB (60) and an annular oil duct II (49); the phase control disc (26) is internally provided with an annular groove A (45) and an annular groove B (54), the annular groove A (45) and the annular groove B (54) are respectively provided with a buffer piston A (46) and a buffer piston B (57), and the buffer piston A (46) and the buffer piston B (57) are in clearance fit with the annular groove A (45) and the annular groove B (54); one end of an arc-shaped spring A (50) and one end of an arc-shaped spring B (56) are respectively fixedly connected with a supporting plate A (48) on a buffer piston A (46) and a supporting plate B (55) on a buffer piston B (57), and the other end of the arc-shaped spring A is respectively connected with the bottom ends of an annular groove A (45) and an annular groove B (54); the buffer rubber A (44) and the buffer rubber B (53) are respectively arranged at the top ends of the annular groove A (45) and the annular groove B (54), and the top ends of the buffer piston A (46) and the buffer piston B (57); the pressure limiting valve A (52) and the pressure limiting valve B (59) are respectively arranged at the bottom ends of the annular groove A (45) and the annular groove B (54); the phase control disc (26) is internally provided with an oil duct IIIA (47), an oil duct IVA (51), an oil duct IIIB (58), an oil duct IVB (60) and an annular oil duct II (49); the annular groove A (45) and the annular groove B (54) are communicated with the annular oil duct II (49) through an oil duct IIIA (47) and an oil duct IIIB (58) respectively; the oil outlets of the pressure limiting valve A (52) and the pressure limiting valve B (59) are communicated with the annular oil duct II (49) through an oil duct IVA (51) and an oil duct IVB (60) respectively; the connecting rod A (22) and the connecting rod B (28) are fixedly connected with the electromagnetic chuck II (20) through threads, and the return spring A (23) and the return spring B (29) are respectively arranged in the cavity A (25) and the cavity B (31) of the cylinder body (33) and respectively contacted with the baffle A (24) and the baffle B (30) on the connecting rod A (22) and the connecting rod B (28); the rubber pad (21) is fixed on the surface of the phase control disc (26), and the friction plate B (19) is fixed on the surface of the electromagnetic chuck II (20).
2. An engine stop phase control mechanism according to claim 1, wherein the fixed shaft (27) is internally provided with an oil passage v (61), a main oil passage (62) and an oil passage vi (63); the main oil duct (62), the oil duct V (61), the annular oil duct I (36), the oil duct IIA (43) and the oil duct IA (42) are communicated with each other; the main oil duct (62), the oil duct V (61), the annular oil duct I (36), the oil duct II B (40) and the oil duct IB (39) are communicated with each other; the main oil duct (62), the oil duct VI (63), the annular oil duct II (49) and the oil duct IIIA (47) are communicated with each other; the main oil duct (62), the oil duct VI (63), the annular oil duct II (49) and the oil duct IIIB (58) are communicated with each other.
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| CN201710235304.XA CN106870173B (en) | 2017-04-12 | 2017-04-12 | Engine shutdown phase control mechanism |
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| CN201710235304.XA CN106870173B (en) | 2017-04-12 | 2017-04-12 | Engine shutdown phase control mechanism |
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| CN106870173B true CN106870173B (en) | 2023-09-19 |
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Inventor after: Jin Zhaohui Inventor after: Yu Qi Inventor after: Feng Shuang Inventor after: Zhao Haiping Inventor after: Wang Andong Inventor after: Xie Fangxi Inventor after: Hong Wei Inventor after: Huang Zhen Inventor after: Su Yan Inventor after: Xu Yun Inventor after: Li Xiaoping Inventor after: Jiang Beiping Inventor after: Kang Erning Inventor before: Xie Fangxi Inventor before: Feng Shuang Inventor before: Zhao Haiping Inventor before: Wang Andong Inventor before: Hong Wei Inventor before: Huang Zhen Inventor before: Su Yan Inventor before: Xu Yun Inventor before: Li Xiaoping Inventor before: Jiang Beiping Inventor before: Kang Erning Inventor before: Yu Qi |
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