CN106762197B - Built-in swing hydraulic motor type variable compression ratio piston - Google Patents
Built-in swing hydraulic motor type variable compression ratio piston Download PDFInfo
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- CN106762197B CN106762197B CN201710156305.5A CN201710156305A CN106762197B CN 106762197 B CN106762197 B CN 106762197B CN 201710156305 A CN201710156305 A CN 201710156305A CN 106762197 B CN106762197 B CN 106762197B
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- piston
- main body
- compression ratio
- pin
- rotating wheel
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
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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
- F02D15/00—Varying compression ratio
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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
- F02D2700/00—Mechanical control of speed or power of a single cylinder piston engine
- F02D2700/03—Controlling by changing the compression ratio
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Abstract
The invention discloses a built-in swing hydraulic motor type variable compression ratio piston, which aims to solve the problems of high manufacturing cost, poor reliability and complex structure in the prior art. The invention is composed of a piston main body, a piston skirt part, a piston pin, a connecting rod, a clamping ring, a blade motor, a sealing cover plate and a spiral rotating wheel; the vane motor is placed on a piston skirt center seat, the vane motor is connected with the spiral rotating wheel through a spline, the internal thread of the piston main body is matched with the external thread of the spiral rotating wheel, the pin hole of the piston main body is parallel to the axis of the pin hole of the piston skirt, the connecting rod is placed in the inner cavity of the piston, and the piston pin is inserted into the pin holes of the small end of the connecting rod, the piston skirt and the piston main body. Hydraulic oil flows through an oil path formed by the connecting rod, the piston pin and the piston skirt portion and then enters the oil cavity, the pressure in the oil cavity pushes the vane motor to drive the spiral rotating wheel, and the spiral rotating wheel enables the piston main body and the piston skirt portion to generate relative displacement under the action of thread fit, so that the compression ratio of the engine is changed.
Description
Technical Field
The invention relates to a piston of an internal combustion engine, in particular to a variable compression ratio piston with a built-in swing hydraulic motor.
Background
The compression ratio determines the pressure of the gasoline engine to compress the mixture, and the combustion characteristic of the gasoline results in that the mixture pressure of the gasoline engine cannot be too high. If the pressure in the cylinder exceeds a threshold value, the gasoline is ignited before ignition due to compression, a phenomenon known as knocking, and knocking occurs, causing great damage to the engine. For supercharged engines which are widely used at present, after the intervention of turbocharging, the temperature and pressure of the combustion chamber can be greatly increased, and if the value is too high, knocking can not be avoided. This can cause significant damage to the engine and also affect power output. Therefore, fixed compression ratio turbocharged and supercharged engines can only be designed with a lower compression ratio than ordinary naturally aspirated engines. However, such an excessively low compression ratio design may result in an engine that has very low combustion efficiency when the supercharger (especially turbo charger) is not fully engaged (i.e., the engine is at a low speed), and may produce much less power than a conventional naturally aspirated engine. This contradiction is an important reason for prompting designers to develop variable compression ratio engines.
In addition, the technology can provide great advantages for the engine in terms of fuel adaptability. The compression ratio of the mainstream engine of the new style at present is generally designed to be more than 10. However, high compression ratio engines require the use of higher grade fuel, which reduces the flexibility of the vehicle in remote locations and affects the sales of the vehicle.
Using variable compression ratio technology enables:
1. the power performance of the engine is improved by improving the thermal efficiency of the engine.
2. The probability of knocking generation is reduced.
3. The engine is convenient to be designed in a miniaturized way.
4. The engine can burn fully and reduce CO 2 And (4) discharging.
Disclosure of Invention
The invention provides a built-in swing hydraulic motor type transformer for solving the technical problems of high manufacturing cost, poor reliability and complex structure in the prior art 1 Compressing the piston.
In order to solve the technical problems, the invention adopts the following technical scheme:
a built-in swing hydraulic motor type piston with variable compression ratio is characterized in that a vane motor is placed in a center seat of a piston skirt part, and a sealing cover plate covers the upper end face of the center seat and is fixed through a bolt; the base of the spiral rotating wheel is positioned at the lower part of the clamping ring groove of the piston skirt part, the clamping ring is placed in the clamping ring groove of the piston skirt part, and the spiral rotating wheel is limited in the direction rotating around the axis of the piston; the piston main body is sleeved on the piston skirt, the axis of a piston main body pin hole is parallel to the axis of a piston skirt pin hole, and the piston main body is in spiral fit with the spiral rotating wheel; the connecting rod is placed in a cavity in the lower portion of the skirt and the wrist pin is inserted into the pin bores in the small end of the connecting rod, the piston body and the skirt.
The pin hole of the piston main body is processed into a runway-shaped elliptical structure.
The upper end surface of the vane motor is provided with a circle of sealing groove with a rectangular cross section, and the outer sides of the inner oil groove and the outer oil groove and the boss of the lower end surface of the vane motor are respectively provided with a circle of sealing groove with a rectangular cross section.
The left side and the right side of the four oil grooves of the piston pin are respectively provided with a circle of sealing grooves.
The sealing grooves of the vane motor and the piston pin are filled with polytetrafluoroethylene O-shaped rings.
The side surface of the vane motor is in clearance fit with the inner wall of the piston skirt central seat, the upper end surface and the lower end surface of the vane motor are also in clearance fit with the bottom surface of the central seat and the sealing cover plate, and the vane motor can freely rotate in an oil cavity of the central seat.
Compared with the prior art, the invention has the beneficial effects that:
1. the built-in swing hydraulic motor type piston with the variable compression ratio utilizes the swing hydraulic motor as a power source, has the characteristics of large torque and small rotation angle, and can ensure the strong power output of the device.
2. The oil way of the piston with the built-in swing hydraulic motor and the variable compression ratio is drilled in the piston, a piston pin, a connecting rod and a crankshaft, so that the change of other places is avoided.
3. The built-in swing hydraulic motor type variable compression ratio piston has good economical efficiency because the original piston and the original combustion chamber are reserved and only the interior of the piston is changed.
4. According to the built-in swing hydraulic motor type variable compression ratio piston, the piston body moves relative to the piston skirt part through the spiral rotating wheel, and due to the self-locking effect of the spiral rotating wheel, the pressure of the cylinder cannot be transmitted to the vane motor, so that the normal operation of the motor vanes is guaranteed, and the work is reliable.
Drawings
The invention is further described with reference to the accompanying drawings in which:
fig. 1 is a front sectional view of a variable compression ratio piston incorporating an oscillating hydraulic motor according to the present invention.
Fig. 2 is a left side view of a variable compression ratio piston with an internal swing hydraulic motor according to the present invention.
Fig. 3 is a top view of the piston skirt of the present invention.
Fig. 4 is a front sectional view of a motor blade of the present invention.
FIG. 5 is a D-D projection view of a front cross-sectional view of a motor blade of the present invention.
FIG. 6 is an E-E projection view of a front cross-sectional view of a motor blade of the present invention.
FIG. 7 is a front view of the piston pin of the present invention.
FIG. 8 is a C-C projection of a front view of the piston pin of the present invention.
FIG. 9 is a front view of the connecting rod of the present invention.
FIG. 10 isbase:Sub>A projection A-A ofbase:Sub>A front view of the linkage of the present invention.
FIG. 11 is a projection B-B of a front view of a connecting rod of the present invention.
In the figure: 1. the piston comprises a piston main body, 2 parts of a spiral rotating wheel, 3 parts of a sealing cover plate, 4 parts of a clamping ring, 5 parts of a piston skirt part, 6 parts of a spline, 7 parts of a vane motor, 8 parts of a connecting rod and 9 parts of a piston pin.
Detailed Description
The invention is described in detail below with reference to the attached drawing figures:
as shown in fig. 1, the vane motor 7 is placed on the center seat of the piston skirt 5, the oil groove on the vane motor 7 is opposite to the oil groove port of the center seat of the piston skirt, and the sealing cover plate 3 is fixed with the center seat of the piston skirt 5 through bolts; the end surface of the vane motor 7 is in clearance fit with the side surface, the inner wall of the central seat and the lower end surface of the sealing cover plate 3, and the vane motor 7 can rotate in the central seat; the upper part of the spline 6 is connected with the helical rotary wheel 2, the lower part of the spline is connected with the vane motor 7, the base of the helical rotary wheel 2 is positioned below the clamping ring groove of the piston skirt part 5, the clamping ring 4 is placed in the clamping ring groove of the piston skirt part 5, and the helical rotary wheel 2 is limited in the direction rotating around the axis of the piston; the piston main body 1 and the spiral rotary wheel 2 are connected in a threaded mode, the pin hole of the piston main body 1 is parallel to the axis of the pin hole of the piston skirt portion 5, the small end of the connecting rod 8 is placed in an inner cavity below the piston skirt portion 5, and the small end of the connecting rod 8, the pin hole of the piston main body 1 and the pin hole of the piston skirt portion 5 are connected together through the piston pin 9.
As shown in fig. 1, 2 and 3, the original piston is divided into an inner part and an outer part, wherein the outer part is a piston main body 1, and the inner part is a piston skirt part 5. The upper part of the inner wall of the piston main body 1 is of an inner spiral structure with a trapezoidal tooth shape, the lower part of the inner wall is polished to be smooth, steps with obvious separation are arranged between the upper part and the lower part of the inner wall, and pin holes in the piston main body 1 are processed into a runway elliptical structure; the middle of the upper portion of the piston skirt portion 5 is protruded to form a center seat, the appearance of the center seat is an open cylinder, the inner wall of the center seat is uniformly distributed with three fixed stators with fan-shaped blade structures, a circle of threaded holes are uniformly distributed on the open end face of the center seat, the left side and the right side of the bottom face of the center seat along the direction perpendicular to the axis of the piston are respectively drilled with a semicircle of oil grooves, an oil channel is drilled from the middle position of the two oil grooves, the oil channel is drilled from a pin hole of the piston skirt portion 5, the outer side of the center seat is a circle of thin-wall-shaped protruding structure, and the inner side of the thin wall is a clamping ring groove with a rectangular cross section.
As shown in fig. 1, the spiral rotor 2 is a cylindrical structure, the outer side surface of the spiral rotor 2 is a trapezoidal thread, the lower part of the spiral rotor is a circular base, a support steel plate is arranged in the middle of the spiral rotor 2, and a splined hole is drilled in the center of the support steel plate.
As shown in fig. 4, 5 and 6, the vane motor 7 is a structure in which three fan-shaped vanes are uniformly distributed on the side surface of a cylinder, the upper end surface of the vane motor 7 is drilled with spline holes and is provided with a circle of sealing grooves with rectangular cross sections, the lower end surface is connected with a cylindrical boss, the side surface of the boss is also provided with a circle of sealing grooves with rectangular cross sections, the lower end surface is drilled with an inner ring oil groove and an outer ring oil groove, the outer ring oil groove is shallow, the inner ring oil groove is deep, the top of the inner ring oil groove and the top of the outer ring oil groove are respectively provided with three oil passages along the vane axial line to the outside, wherein the three oil passages of the inner ring oil groove are vertical to the vane axial line to drill vanes, the three oil passages of the outer ring oil groove are vertical to the vane axial line to drill vanes in the opposite direction, and the outer side of the opening of the outer oil groove is respectively provided with a circle of sealing grooves with rectangular cross sections in the lower end surface of the vane motor 7.
As shown in fig. 1, 7 and 8, the piston pin 9 of the original machine is reworked, the oil passages in the piston pin 9 are arranged in a bilateral symmetry structure, the piston pin 9 is provided with a circle of rectangular-section oil grooves at the contact position with the oil passage opening at the left side of the pin hole of the piston skirt 5, the piston pin 9 is provided with a circle of rectangular-section oil grooves at the contact position with the oil passage opening at the left side of the small end of the connecting rod 8, four short oil passages are respectively drilled at the bottoms of the two circles of oil grooves inwards along the direction vertical to the axis of the piston pin 9, and the eight short oil passages are connected through four long oil passages parallel to the axis of the piston pin 9.
As shown in fig. 9, 10 and 11, the connecting rod 8 of the original machine is reworked, and the left and right diagonal lines of the rod body of the connecting rod 8 are respectively drilled with an oil passage by taking the large end of the connecting rod 8 as an inlet and the small end of the connecting rod 8 as an outlet.
The crankshaft of the original machine is reprocessed, two oil ducts are drilled from the shaft end of the crankshaft, and the oil ducts are drilled along the crankshaft journal, and the position of an oil duct opening of the crankshaft journal is opposite to the position of an oil duct opening of the large end of the connecting rod.
As shown in fig. 1, 2, and 3, when the engine needs a large compression ratio, the hydraulic oil pump guides hydraulic oil into the left oil passage of the connecting rod 8 through the crankshaft, sequentially passes through four oil passages on the left side of the piston pin 9 and the left oil passage of the piston main body 1, enters the outer oil groove of the vane motor 7, and then enters three oil chambers formed by the center seat of the piston skirt 5 and the vane motor 7 through three oil passages connected with the outer oil groove, with the increase of the hydraulic oil pressure, the oil chambers are pressed to push the vane motor 7 to rotate, the spline 6 transmits the power of the vane motor 7 to the helical rotation wheel 2, so that the helical rotation wheel 2 rotates along with the helical rotation, the external thread of the helical rotation wheel 2 is in helical fit with the internal thread of the piston main body 1, so that the piston main body 1 is separated from the piston skirt 5 under the guiding action of the piston pin 9, and the compression ratio of the engine is increased at this time.
As shown in fig. 1, 2 and 3, when the engine needs a low compression ratio, similarly, hydraulic oil is introduced into the right oil passage of the connecting rod 8, sequentially passes through the right oil passage of the piston pin 9 and the right oil passage of the piston main body 1, enters the inner oil groove of the vane motor 7, and then enters three opposite oil chambers formed by the central seat and the vane motor 7 through three oil passages connected with the inner oil passage, after the pressure of the oil chambers is increased, the vane motor 7 is pushed to rotate in the opposite direction, the spiral rotating wheel 2 rotates along with the spiral rotating wheel 2, the spiral rotating wheel 2 is in spiral fit with the piston main body 1, so that the piston main body 1 is folded relative to the piston skirt portion 5 under the guiding action of the piston pin 9, and the compression ratio of the engine is reduced.
As shown in fig. 1, 2 and 3, when the engine completes the change of the compression ratio, the hydraulic oil pump stops working, at this time, the pressure of the oil chamber formed by the central seat of the piston skirt 5 and the vane motor 7 is maintained constant, the cylinder pressure generated by violent combustion acts on the top of the piston main body 1, and due to the self-locking property of the internal screw of the piston main body 1, the combustion pressure does not forcibly push the piston main body 1 to move relative to the piston skirt 5, and at this time, the compression ratio of the engine is maintained constant.
Claims (6)
1. The piston is characterized in that the piston comprises a piston main body (1), a spiral rotating wheel (2), a sealing cover plate (3), a snap ring (4), a piston skirt portion (5), a spline (6), a vane motor (7), a connecting rod (8) and a piston pin (9);
the vane motor (7) is placed in a center seat of the piston skirt part (5), and the sealing cover plate (3) is placed on the upper end face of the center seat and fixed through bolts; the upper part and the lower part of the spline (6) are respectively connected with the spiral rotating wheel (2) and the blade motor (7), the base of the spiral rotating wheel (2) is positioned at the lower part of the clamping ring groove of the piston skirt part (5), the clamping ring (4) is placed in the clamping ring groove of the piston skirt part (5), and the spiral rotating wheel (2) is limited in the direction rotating around the axis of the piston; the piston main body (1) is sleeved on the piston skirt portion (5), the piston main body (1) is in threaded fit with the spiral rotating wheel (2), and the axis of a pin hole of the piston main body (1) is parallel to the axis of a pin hole of the piston skirt portion (5); a connecting rod (8) is placed in a cavity below a piston skirt portion (5), and a piston pin (9) is inserted into a small end of the connecting rod (8), a piston main body (1) and a pin hole of the piston skirt portion (5).
2. A variable compression ratio piston with an internally-arranged oscillating hydraulic motor according to claim 1, characterized in that the pin hole of the piston body (1) is formed into a racetrack-shaped oval structure.
3. A variable compression ratio piston with an internally mounted oscillating hydraulic motor as claimed in claim 1, wherein the vane motor is a three-vane rotor design, the upper end face of the vane motor (7) has a circle of sealing groove with rectangular cross section, and the outer sides of the inner and outer oil grooves and the side face of the boss on the lower end face of the vane motor have a circle of sealing groove with rectangular cross section.
4. A piston with a built-in oscillating hydraulic motor and variable compression ratio as claimed in claim 1, wherein the left and right sides of the four oil grooves of the piston pin (9) are respectively provided with a circle of sealing grooves with rectangular sections.
5. A variable compression ratio piston with an internally-arranged oscillating hydraulic motor according to claim 1, characterized in that the filling material in the sealing groove of the vane motor (7) and the sealing groove of the piston pin (9) is a teflon O-ring.
6. A variable compression ratio piston with an internally mounted oscillating hydraulic motor as claimed in claim 1, wherein the vane motor (7) has its side surfaces in clearance fit with the inner wall of the center seat of the skirt portion (5), and the upper and lower end surfaces of the vane motor (7) are also in clearance fit with the bottom surface of the center seat and the sealing cover plate (3), and the vane motor (7) is rotatable in the oil chamber of the center seat.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710156305.5A CN106762197B (en) | 2017-03-16 | 2017-03-16 | Built-in swing hydraulic motor type variable compression ratio piston |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710156305.5A CN106762197B (en) | 2017-03-16 | 2017-03-16 | Built-in swing hydraulic motor type variable compression ratio piston |
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| Publication Number | Publication Date |
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| CN106762197A CN106762197A (en) | 2017-05-31 |
| CN106762197B true CN106762197B (en) | 2023-03-24 |
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| CN201710156305.5A Active CN106762197B (en) | 2017-03-16 | 2017-03-16 | Built-in swing hydraulic motor type variable compression ratio piston |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN107725210A (en) * | 2017-11-24 | 2018-02-23 | 吉林大学 | A kind of variable-compression-ratio piston with restraining position ring block structure |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4283271B2 (en) * | 2005-12-28 | 2009-06-24 | 本田技研工業株式会社 | Variable compression ratio device for internal combustion engine |
| FR2939844B1 (en) * | 2008-12-11 | 2010-12-24 | Peugeot Citroen Automobiles Sa | INTERNAL COMBUSTION ENGINE WITH VARIABLE GEOMETRY COMBUSTION CHAMBER. |
| KR101500392B1 (en) * | 2013-12-13 | 2015-03-09 | 현대자동차 주식회사 | Variable compression ratio device |
| CN105370417B (en) * | 2015-12-07 | 2018-02-23 | 吉林大学 | Variable lift compression ratio piston |
| CN105604728B (en) * | 2016-01-20 | 2017-12-26 | 吉林大学 | Motor drives slide block type compression ratio piston |
| CN105673203B (en) * | 2016-04-07 | 2017-12-15 | 吉林大学 | A kind of ratchet drive-type variable-compression-ratio piston link assembly |
| CN105927396B (en) * | 2016-06-07 | 2018-08-17 | 吉林大学 | A kind of new type of compression compares piston rod part |
| CN206555023U (en) * | 2017-03-16 | 2017-10-13 | 吉林大学 | A kind of built-in rotary actuator formula Ratios piston |
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