CN106837592B - Double-screw transmission type variable compression ratio piston - Google Patents
Double-screw transmission type variable compression ratio piston Download PDFInfo
- Publication number
- CN106837592B CN106837592B CN201710245566.4A CN201710245566A CN106837592B CN 106837592 B CN106837592 B CN 106837592B CN 201710245566 A CN201710245566 A CN 201710245566A CN 106837592 B CN106837592 B CN 106837592B
- Authority
- CN
- China
- Prior art keywords
- piston
- blade
- piston skirt
- screw
- inner sleeve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- 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
- F02F3/0015—Multi-part pistons
- F02F3/0023—Multi-part pistons the parts being bolted or screwed together
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/044—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of an adjustable piston length
Landscapes
- 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)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
The invention discloses a double-screw transmission type variable compression ratio piston, which aims to solve the problems of high manufacturing cost, high energy loss, unreliable work and high installation difficulty in the prior art; the invention is composed of a piston assembly, a transmission part and a hydraulic actuating mechanism, wherein the piston assembly is divided into a piston top and a piston skirt, the transmission part is a spiral inner sleeve and a spline, and the hydraulic actuating mechanism is a blade rotor and a blade stator; hydraulic oil introduced from the connecting rod enters a cavity formed between the vane stator and the vane rotor to push the vane rotor to rotate and drive the spiral inner sleeve to rotate, and on the premise of guiding the piston pin, the spiral inner sleeve drives the top of the piston to separate or fold relative to the piston skirt, so that the compression ratio of the engine is increased or reduced; the double-spiral inner sleeve ensures convenient installation, reduces the cost by changing the structure on the piston, and has reliable work by using the hydraulic mechanism as an actuating mechanism.
Description
Technical Field
The invention discloses a piston of an engine for a vehicle, in particular to a double-screw transmission type variable compression ratio piston.
Background
In recent years, the increasingly stringent energy crisis and emission regulations place higher demands on the performance of engines, and in order to accommodate these new demands, while allowing the engines to have better power, fuel economy and emissions, variable compression ratio technology is more important.
In general, the higher the compression ratio of the engine, the longer the distance of the piston working stroke, the more work done and the greater the output power. However, excessive compression ratio in gasoline engines can lead to uncontrolled combustion, thereby damaging the engine and being prone to knock when the load is relatively large; the excessive compression ratio in the diesel engine leads to the excessive high pressure of the cylinder of the diesel engine, so that the vibration noise is aggravated, and the impact load born by the moving parts is increased, thereby influencing the working reliability and the service life of the diesel engine. Therefore, it is necessary to employ a variable compression ratio technique according to a variation in engine load.
The variable compression ratio technique can be used:
1. the heat efficiency of the engine is improved, and the economy of the engine is greatly improved.
2. Since a large part of harmful emissions of the engine are generated and the engine is cold-started and warmed-up, the variable compression ratio technique can shorten the time of the cold-start and warm-up phases, thereby reducing the harmful emissions of the engine
3. The variable compression ratio technology combines the economy under partial load and the dynamic performance under large load, so that the dynamic performance, economy and emission performance of the engine are better unified.
Disclosure of Invention
The invention provides a double-screw transmission type variable compression ratio piston, which solves the technical problems of high manufacturing cost, unreliable work and inconvenient installation in the prior art.
In order to solve the technical problems, the invention is realized by adopting the following technical scheme:
the double-screw transmission type variable compression ratio piston comprises the components including a piston top, a screw inner sleeve, a blade baffle, a blade rotor, a spline, a piston skirt, a piston pin and a connecting rod;
the blade rotor is arranged in the blade stator in the center of the piston skirt, the blade baffle is arranged on the upper end surface of the blade stator, the oil hole on the blade baffle is opposite to the oil hole on the upper end surface of the blade stator, and the blade baffle is fixed with the blade stator by bolts; the lower part of the spline is connected with the blade rotor, the upper part of the spline is connected with the spiral inner sleeve in a pin key way, the top of the piston is sleeved on the piston skirt, the internal thread of the spiral inner sleeve is in spiral fit with the external thread of the blade stator of the piston skirt, and the external thread of the spiral inner sleeve is in spiral fit with the internal thread of the top of the piston; the pin hole axis of the piston top is parallel to the pin hole axis of the piston skirt, and the piston pin connects the small end of the connecting rod, the pin hole of the piston skirt and the pin hole of the piston top.
The spiral inner sleeve (2) is of a cylindrical structure with a supporting plate in the middle, the outer side of the cylinder is an outer spiral with a trapezoid cross section, the lower part of the supporting plate is also an outer spiral with a trapezoid cross section on the inner side of the cylinder, and the upper wall surface of the supporting plate is smooth.
The left side of the pin hole surface of the piston skirt part is drilled with an oil way along the direction parallel to the axis of the piston, the oil way is divided into three oil ways after passing through an arc-shaped sealing oil groove to enter the lower connection part of the inner wall of the vane stator and the vane stator vane, the right side of the pin hole surface of the piston skirt part is drilled with an oil way along the direction parallel to the axis of the piston, and the oil way is upwards up to the upper end face of the vane stator.
The blade baffle plate is drilled with an oil hole, the position of the oil hole is opposite to the oil hole on the upper end face of the blade stator, and the oil hole on the blade baffle plate is divided into three oil ways to enter the upper connection part of the inner wall of the blade stator and the blade stator vane fan after passing through an arc-shaped sealing oil groove.
The outer side of the vane stator of the piston skirt is provided with an external thread with a trapezoid cross section, and the thread screwing direction is the same as that of the external thread of the spiral inner sleeve.
Compared with the prior art, the invention has the beneficial effects that:
1. the double-screw transmission type variable compression ratio piston provided by the invention has the advantages that the double-screw inner sleeve is adopted as a transmission part, the characteristics of a screw structure are utilized for restraining, and the installation is convenient.
2. The double-screw transmission type variable compression ratio piston increases torque by utilizing the hydraulic mode of the swing blade, and drives the relative movement of the top of the piston and the skirt part of the piston by utilizing the screw structure, so that the double-screw transmission type variable compression ratio piston is reliable in operation.
3. The double-screw transmission type variable compression ratio piston disclosed by the invention is used for processing only the piston, is additionally provided with the driving device and the drilling oil way, and is short in processing time and low in manufacturing cost.
Drawings
The invention is further described below with reference to the accompanying drawings:
fig. 1 is a front sectional view of a double screw driving type variable compression ratio piston according to the present invention.
Fig. 2 is a left side view of a double screw drive variable compression ratio piston according to the present invention.
Fig. 3 is a top view of the present invention showing the mating of a vane rotor with a vane stator of a piston skirt.
FIG. 4 is a front cross-sectional view of a piston skirt part of the present invention.
FIG. 5 is an E-E projection view of a front cross-sectional view of a piston skirt assembly of the present invention.
FIG. 6 is a front cross-sectional view of a vane baffle of the present invention
FIG. 7 is a C-C projection view of a front cross-sectional view of a blade baffle of the present invention.
Fig. 8 is a front view of the wrist pin of the present invention.
Fig. 9 is a view of the piston pin of the present invention from the front view C-C.
In the figure: 1. the piston comprises a piston top, a spiral inner sleeve, a blade baffle, a blade rotor, a spline, a piston skirt, a piston pin and a connecting rod.
Detailed Description
The invention is described in detail below with reference to the attached drawing figures:
as shown in fig. 3, fig. 4 and fig. 5, the piston skirt 6 is made by investment casting, the central bulge of the piston skirt 6 is a vane stator, the outer wall of the vane stator is processed into a trapezoid outer spiral structure, the inner wall of the vane stator is fixedly provided with three fan-shaped vane structures, the vane stator is just matched with the vane rotor 4, the upper end surface of the vane stator is provided with a circle of threaded holes from top to bottom, the left side pin hole inner wall of the piston skirt 6 is drilled with an oil hole, the oil hole is upward, and then after horizontal passes through a large half circle of circular arc-shaped hollow oil grooves, three oil paths are equally distributed to enter the joint of the inner wall of the vane stator and the three fan-shaped structures, the right side pin hole inner wall of the piston skirt 6 is drilled with the oil hole upward, and the upper end surface of the vane stator is drilled with the oil hole.
As shown in fig. 6 and 7, the blade baffle 3 is provided with uniform countersunk holes, the positions of the countersunk holes are just right opposite to threaded holes at the upper end of the blade stator, in addition, the right side of the blade baffle 3 is provided with an oil hole, the positions of the countersunk holes are just right opposite to oil holes at the upper end face of the blade stator, the oil hole of the blade baffle 3 is horizontally divided into three oil ways through a majority of circular arc-shaped oil grooves, and the three oil ways respectively enter the other three joints of the blade stator and the inner wall.
As shown in fig. 1 and 2, the piston top 1 is reprocessed by a conventional piston, a large cavity is formed in the middle of the piston top 1, the inner wall of the upper side of the piston top 1 is an internal thread with trapezoidal teeth, the lower side wall surface is smooth, and the pin hole of the piston top 1 is reprocessed into a racetrack-shaped elliptical structure.
As shown in fig. 1, the spiral inner sleeve 2 has a cylindrical structure, a supporting plate with a splined hole is arranged in the middle of the cylinder, and the outer wall of the cylinder is provided with external threads with trapezoidal teeth; the screw thread screwing direction is the same as the external screw thread screwing direction of the blade stator; the inner wall of the cylinder, the lower part of the supporting plate is an internal thread with trapezoidal tooth shape, and the upper end of the supporting plate is a smooth wall surface.
Two oil ways are drilled in the diagonal direction of the rod body of the connecting rod 8, the two oil ways are drilled from the large end of the connecting rod 8 and the small end of the connecting rod 8, two oil ways are also communicated in the crankshaft, the two oil ways are drilled from the radial direction of the left main shaft and the right main shaft respectively, the two oil ways are drilled from the radial direction of the shaft of the connecting rod, and a hydraulic oil pump is connected with the oil ways of the main journal.
As shown in fig. 1, 8 and 9, oil paths with symmetrical left and right sides are drilled in the piston pin 7, the piston pin 7 of the original machine is reprocessed, a circle of rectangular-section oil grooves are formed in the contact positions of the piston pin 7 and the left and right side oil ports of the pin hole of the piston skirt 6, a circle of rectangular-section oil grooves are formed in the contact positions of the piston pin 7 and the left and right side oil ports of the small end of the connecting rod 8, the two oil grooves are connected through eight oil paths which are uniformly distributed along the axis direction of the piston, and sealing grooves with rectangular sections are formed in the left and right sides of each oil groove of the piston pin 7.
As shown in fig. 1, the vane rotor 4 is placed in the vane stator of the piston skirt 6, the vane baffle 3 is placed above the vane stator, the oil hole on the vane baffle 3 is opposite to the oil hole on the vane stator, the vane baffle and the vane stator 3 are fixedly sealed by threads, the vane rotor 4 can freely rotate in the vane stator by seventy five degrees, and a space between the vane stator and the vane rotor 4 is a hydraulic oil cavity; one end of the spline 5 is connected with a spline groove on the vane rotor 3, the other end of the spline 5 is connected with the spiral inner sleeve 2 through a pin key, and the internal thread of the spiral inner sleeve 2 is matched with the external thread of the piston skirt 6; sleeving the piston top 1 on the piston skirt 6, and enabling the internal thread of the piston top 1 to be matched with the external thread of the spiral inner sleeve 2, wherein the pin hole axis of the piston top 1 is parallel to the pin hole axis of the piston skirt 6; the connecting rod 8 is placed in a cavity at the lower part of the piston skirt 6, and then the piston pin 7 is inserted into the small end of the connecting rod 8, the pin hole of the piston top 1 and the pin hole of the piston skirt 6; the direction of the oil path sequentially passes through a crank oil path, a connecting rod 8 oil path, a piston pin 7 oil path and a piston skirt 6 oil path, and finally enters the hydraulic oil cavity.
As shown in fig. 1, when the engine needs an increased compression ratio, the hydraulic pump starts to rotate positively, hydraulic oil passes through a crankshaft, a connecting rod 8, a piston pin 7 and an oil path on the left side of the piston skirt 6, finally reaches the circular arc-shaped oil groove of the piston skirt 6, and is divided into three oil paths to enter three hydraulic oil chambers formed by the vane stator and the vane rotor 4. The pressure of the hydraulic oil cavity is increased to push the vane rotor 4 to rotate anticlockwise, the vane rotor 4 pushes the spiral inner sleeve 2 to rotate anticlockwise through the connection of the spline 5, and because the spiral inner sleeve 2 is in threaded fit with the vane stator, the spiral inner sleeve 2 rises upwards relative to the piston skirt 6 while rotating, and meanwhile, the spiral inner sleeve 2 is in threaded fit with the piston top 1, and the piston top 1 rises upwards relative to the spiral inner sleeve 2 under the guiding action of the piston pin 7. The total amount of rise of the piston crown 1 with respect to the piston skirt 6 is equal to the amount of rise of the piston crown 1 with respect to the screw inner sleeve 2 and the amount of rise of the screw inner sleeve 2 with respect to the piston skirt 6, at which time the engine compression ratio increases.
When the compression ratio of the engine needs to be reduced, as shown in fig. 1, the hydraulic pump is reversed, hydraulic oil passes through a crankshaft, a connecting rod 8, a piston pin 7 and an oil way on the right side of a piston skirt 6, reaches an arc-shaped oil groove of a blade baffle 3 and is divided into three oil ways to enter the hydraulic oil cavity, the blade rotor 4 is pushed to rotate clockwise, the blade rotor 4 transmits torque to the spiral inner sleeve 2 through a spline 5, the spiral inner sleeve 2 rotates and descends downwards relative to a blade stator, and the spiral inner sleeve 2 is matched with the piston top 1 through threads, and the piston top 1 descends downwards relative to the spiral inner sleeve 2 under the guiding action of the piston pin 7. The total amount of lowering of the piston crown 1 relative to the piston skirt 6 is equal to the amount of lowering of the piston crown 2 relative to the spiral inner sleeve 3 and the amount of lowering of the spiral inner sleeve 3 relative to the piston skirt 6, at which time the engine compression ratio is reduced.
When the engine compression ratio change has been completed and it is desired to keep the compression ratio unchanged, the hydraulic pump is stopped, at which time the hydraulic oil of the entire piston does not flow relatively, and the piston crown 1 will remain stationary with respect to the piston skirt 6 due to the self-locking of the screw structure of the threaded inner sleeve 2, at which time the compression ratio of the engine will not change, as shown in fig. 1.
Claims (3)
1. The double-screw transmission type variable compression ratio piston is characterized by comprising a piston top (1), a screw inner sleeve (2), a blade baffle (3), a blade rotor (4), a spline (5), a piston skirt (6), a piston pin (7) and a connecting rod (8), wherein the blade rotor (4) is placed in a blade stator structure in the center of the piston skirt (6), the blade baffle (3) is placed on the upper end face of the blade stator structure in the center of the piston skirt (6), an oil hole on the blade baffle (3) is opposite to an oil hole on the upper end face of the blade stator structure in the center of the piston skirt (6), the blade baffle (3) is fixed with the blade stator structure in the center of the piston skirt (6) by a bolt, the lower part of the spline (5) is connected with the blade rotor (4), the upper part of the spline (5) is connected with the screw inner sleeve (2) in a key way, the piston top (1) is sleeved on the piston skirt (6), the inner thread of the screw inner sleeve (2) is in screw fit with the outer thread of the blade stator structure in the piston skirt (6), and the outer thread of the screw inner thread of the piston skirt (2) is in screw fit with the inner thread of the piston pin (1). The pin hole axis of piston top (1) is parallel with the pin hole axis of piston skirt (6), piston pin (7) links up connecting rod (8) tip, piston skirt (6) pinhole, piston top (1) pinhole, the left side of the pinhole surface of piston skirt (6) has the oil circuit along parallel piston axis direction brill, after the oil circuit level passes through a convex sealed oil groove, divide into three oil circuit and get into the blade stator structure inner wall at piston skirt (6) center and the lower junction of blade stator structure leaf fan, the pinhole surface right side of piston skirt (6) has the oil circuit along parallel piston axis direction brill, the oil circuit upwards reaches the up end of blade stator structure at piston skirt (6) center, it is just right with the up end oilhole of blade stator structure at piston skirt (6) center to bore on blade baffle (3), the oilhole level on blade baffle (3) is through a convex sealed oil groove after, divide into three oil circuit and get into the blade stator structure inner wall at piston skirt (6) center and the offside junction on the opposite side of blade stator structure leaf fan.
2. A double-screw driving variable compression ratio piston according to claim 1, characterized in that the screw inner sleeve (2) is of a cylindrical structure with a support plate in the middle, the outside of the cylinder is an outer screw with a trapezoidal cross section, the lower part of the support plate is also an outer screw with a trapezoidal cross section inside the cylinder, and the upper wall surface of the support plate is smooth.
3. A double-screw drive variable compression ratio piston according to claim 1, characterized in that the outer side of the vane stator structure of the piston skirt (6) is an external screw thread with a trapezoidal cross section, and the screw thread direction is the same as the external screw thread direction of the screw inner sleeve (2).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710245566.4A CN106837592B (en) | 2017-04-14 | 2017-04-14 | Double-screw transmission type variable compression ratio piston |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710245566.4A CN106837592B (en) | 2017-04-14 | 2017-04-14 | Double-screw transmission type variable compression ratio piston |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106837592A CN106837592A (en) | 2017-06-13 |
| CN106837592B true CN106837592B (en) | 2023-05-09 |
Family
ID=59146984
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710245566.4A Active CN106837592B (en) | 2017-04-14 | 2017-04-14 | Double-screw transmission type variable compression ratio piston |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN106837592B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107829819B (en) * | 2017-12-15 | 2023-11-17 | 吉林大学 | Vane type hydraulic driving variable compression ratio connecting rod |
| CN108381215A (en) * | 2018-05-17 | 2018-08-10 | 杭州亚太智能装备有限公司 | The rotary bearing support cylinder of hydraulically operated fixture processed for caliper class part in automotive brake |
| CN109184937B (en) * | 2018-11-13 | 2021-02-12 | 滨州渤海活塞有限公司 | Steel piston |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201443440U (en) * | 2009-05-26 | 2010-04-28 | 李志强 | Variable compression ratio piston |
| CN105370417A (en) * | 2015-12-07 | 2016-03-02 | 吉林大学 | Piston with variable lift compression ratio |
| CN105673203A (en) * | 2016-04-07 | 2016-06-15 | 吉林大学 | Ratchet wheel-driven variable compression ratio piston connecting rod assembly |
| CN105927396A (en) * | 2016-06-07 | 2016-09-07 | 吉林大学 | Piston-and-connecting-rod assembly adopting novel compression ratio |
| CN106481477A (en) * | 2016-10-18 | 2017-03-08 | 吉林大学 | A kind of hydraulic motor-driven variable-compression-ratio piston |
| CN206647181U (en) * | 2017-04-14 | 2017-11-17 | 吉林大学 | A kind of double helix driven type Ratios piston |
-
2017
- 2017-04-14 CN CN201710245566.4A patent/CN106837592B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN201443440U (en) * | 2009-05-26 | 2010-04-28 | 李志强 | Variable compression ratio piston |
| CN105370417A (en) * | 2015-12-07 | 2016-03-02 | 吉林大学 | Piston with variable lift compression ratio |
| CN105673203A (en) * | 2016-04-07 | 2016-06-15 | 吉林大学 | Ratchet wheel-driven variable compression ratio piston connecting rod assembly |
| CN105927396A (en) * | 2016-06-07 | 2016-09-07 | 吉林大学 | Piston-and-connecting-rod assembly adopting novel compression ratio |
| CN106481477A (en) * | 2016-10-18 | 2017-03-08 | 吉林大学 | A kind of hydraulic motor-driven variable-compression-ratio piston |
| CN206647181U (en) * | 2017-04-14 | 2017-11-17 | 吉林大学 | A kind of double helix driven type Ratios piston |
Also Published As
| Publication number | Publication date |
|---|---|
| CN106837592A (en) | 2017-06-13 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP4578520B2 (en) | Rotary piston engine and vehicle with this type of engine | |
| CN106837592B (en) | Double-screw transmission type variable compression ratio piston | |
| CN105840303B (en) | A kind of variable-compression-ratio piston link assembly of excentric sleeve transmission | |
| US6776135B1 (en) | Rotary engine | |
| KR20110037394A (en) | Variable compression ratio device | |
| CN112879159B (en) | Internal combustion engine with Tesla valve structure | |
| CN106762196B (en) | Hydraulic motor driven variable compression ratio piston | |
| CN105927396B (en) | A kind of new type of compression compares piston rod part | |
| US20030010312A1 (en) | Internal combustion four cycle rotary engine based on a rotary movement that can be used to make a compressor, a vacuum pump, a steam engine and a high pressure water motor | |
| CN205370438U (en) | Gas drilling screw rod drilling tool of gas drive liquid self -loopa | |
| CN108571381B (en) | Three-stroke internal-cooling rotor engine | |
| JP2016017489A (en) | Internal combustion engine control unit | |
| CN112502828B (en) | Variable compression ratio drive structure | |
| CN106870052B (en) | Variable compression ratio mechanism of engine and valve system matched with variable compression ratio mechanism | |
| CN205638695U (en) | Driven variable compression ratio piston link assembly of eccentric sleeve | |
| CN206647181U (en) | A kind of double helix driven type Ratios piston | |
| CN110617146B (en) | Link mechanism and engine | |
| CN208169323U (en) | A kind of motor-driven variable length link of guide | |
| CN106884734B (en) | Variable compression ratio piston with shaft sleeve | |
| CN109944687A (en) | A kind of three-apexed rotor of rotary polygonal piston engine | |
| WO2010084831A1 (en) | Piston engine with part for covering bottom surface of cap portion of mushroom valve | |
| CN106762197B (en) | Built-in swing hydraulic motor type variable compression ratio piston | |
| CN211737291U (en) | Variable compression ratio drive structure | |
| CN207315656U (en) | A kind of three chamber cam compressors | |
| CN113958405B (en) | High-efficiency oil-saving internal combustion engine |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |