CN114526916A - Stirling engine cylinder pressure detection system and detection method thereof - Google Patents
Stirling engine cylinder pressure detection system and detection method thereof Download PDFInfo
- Publication number
- CN114526916A CN114526916A CN202210421269.1A CN202210421269A CN114526916A CN 114526916 A CN114526916 A CN 114526916A CN 202210421269 A CN202210421269 A CN 202210421269A CN 114526916 A CN114526916 A CN 114526916A
- Authority
- CN
- China
- Prior art keywords
- cylinder
- stirling engine
- crankshaft
- pressure
- phase
- 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.)
- Granted
Links
Images
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M15/00—Testing of engines
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01L—MEASURING FORCE, STRESS, TORQUE, WORK, MECHANICAL POWER, MECHANICAL EFFICIENCY, OR FLUID PRESSURE
- G01L19/00—Details of, or accessories for, apparatus for measuring steady or quasi-steady pressure of a fluent medium insofar as such details or accessories are not special to particular types of pressure gauges
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M15/00—Testing of engines
- G01M15/02—Details or accessories of testing apparatus
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
Abstract
The invention relates to the technical field of engines, in particular to a cylinder pressure detection system of a Stirling engine and a detection method thereof, wherein the pressure detection system comprises the Stirling engine, a working medium pressure detection unit and a crankshaft angle measurement unit, connecting pieces are arranged among cylinders of the engine, one end of each connecting piece is communicated with a hot cavity of each cylinder, the other end of each connecting piece is communicated with a cold cavity of an adjacent cylinder, when the connecting pieces are in a communicated state, the hot cavity of each cylinder is communicated with the cold cavity of the adjacent cylinder, and when the connecting pieces are in a blocked state, the hot cavity of each cylinder is disconnected with the cold cavity of the adjacent cylinder; the working medium pressure detection unit is fixed on a detected cylinder of the Stirling engine, and the crankshaft rotation angle measurement unit is fixed on the Stirling engine.
Description
Technical Field
The invention relates to the technical field of engines, in particular to a cylinder pressure detection system of a Stirling engine and a detection method thereof.
Background
The Stirling engine is a typical external combustion engine and has the characteristics of smooth combustion, wide fuel adaptability, low vibration noise and the like. The fuel is continuously combusted in the combustion chamber outside the cylinder of the Stirling engine, the acting load of the piston is close to a sine wave, so that knocking and intermittent combustion are avoided, the quality advantage in the aspect of low vibration noise is obvious, and the Stirling engine is continuously applied to military and civil fields such as underwater power, landfill power generation, combined heat and power supply and the like from the beginning of the eighties of the last century.
In order to facilitate the research on the combustion process, the heat transfer process between gas and cylinder wall and the intake and exhaust processes in the cylinder of a cylinder engine, the cylinder pressure of a traditional internal combustion engine (such as a diesel engine) is generally reflected by a P-phi indicator diagram (P is the cylinder working medium pressure, and phi is a crank angle), and the P-phi indicator diagram reflects the thermodynamic conversion process of the output mechanical work. The cylinder pressure can be used for researching that the engine pressure is an important basis for calculating engine performance parameters (such as indicated power, explosion pressure, compression pressure and the like) and in-cylinder temperature and the like, and is also an evaluation parameter of an engine heat release rule analysis and combustion process simulation calculation model, and the monitoring and diagnosis of the working state of the engine can be realized by using a cylinder pressure signal. In general, the cylinder working fluid pressure P is measured by a pressure sensor mounted on the cylinder, and the crank angle phi is measured by a flywheel ring gear directly connected thereto.
Meanwhile, the top dead center is a relative reference of the operation position of the crankshaft, and in the test of the pressure of the engine cylinder, the top dead center phase of the P-phi indicator diagram needs to be aligned, and the top dead center aligning method comprises a static top dead center positioning method and a pure compression line method. The static upper dead center positioning method is simple to operate, but because the engine is acted by the gas pressure in the cylinder and the reciprocating inertia force during the operation, the transmission mechanism is easy to generate stress deformation, so that the upper dead center position of the engine during the operation and the position during the static measurement have a certain difference, the static upper dead center positioning method ignores the deformation of the transmission mechanism, and the measurement precision is also influenced by the magnetic wedge and the installation precision of the sensor. The pure compression line method is characterized in that fuel oil injection of a certain cylinder of the engine is stopped, the pressure of the pure compression cylinder and a top dead center pulse signal and a crank angle signal of a flywheel end are synchronously measured, a difference value between a crank angle position corresponding to the peak value of the pressure of the cylinder and the top dead center pulse signal is obtained, and the top dead center pulse signal is corrected during subsequent cylinder pressure measurement. The pure compression line method considers the influence of factors such as measurement errors caused by load and sensor installation, and the measurement precision is high.
However, the stirling engine belongs to a closed cycle engine, the structure of the stirling engine is different from that of a traditional internal combustion engine, a plurality of cylinders are arranged in the engine, pistons are arranged in the cylinders and are connected with a crankshaft through connecting rods, coolers are arranged among the cylinders, the pistons separate the upper side and the lower side of each cylinder to form a hot cavity and a cold cavity, the pistons reciprocate under the action of working medium pressure difference in the hot cavities and the cold cavities to drive the crankshaft to rotate, and the hot cavities of the cylinders are communicated with the cold cavities of adjacent cylinders through the coolers, so that the cylinders are communicated in sequence, and the pure compression line test cannot be carried out to find the phase of the top dead center of the cylinder by stopping a certain cylinder of the engine from injecting fuel into the cylinder like the traditional internal combustion engine (such as a diesel engine). Meanwhile, a crankshaft of the stirling engine is arranged in a crankcase, an output shaft of the engine is arranged in parallel with the crankshaft, a flywheel is arranged at the end of the output shaft, a driving gear is fixed on the crankshaft, a driven gear meshed with the driving gear is fixed on the output shaft, and the crankshaft drives the output shaft to rotate through the driving gear and the driven gear.
Disclosure of Invention
The invention aims to overcome the technical defects, provides a cylinder pressure detection system of a Stirling engine and a detection method thereof, and solves the technical problem that the performance analysis and the dynamic characteristic analysis of the Stirling engine are inconvenient due to the fact that the relation between the cylinder pressure and the crank angle is difficult to obtain when the top dead center of the Stirling engine is taken as a reference in the prior art.
In order to achieve the technical purpose, the technical scheme of the invention provides a cylinder pressure detection system of a Stirling engine, which comprises the Stirling engine, a working medium pressure detection unit and a crankshaft angle measurement unit, wherein a connecting piece is arranged between cylinders of the Stirling engine, one end of the connecting piece is communicated with a hot cavity of each cylinder, the other end of the connecting piece is communicated with a cold cavity of an adjacent cylinder, the connecting piece is a blocking piece with a communicated state or a communicating piece with a communicated state, when the connecting piece is the blocking piece, the hot cavity of each cylinder is disconnected with the cold cavity of the adjacent cylinder, and when the connecting piece is the communicating piece, the hot cavity of each cylinder is communicated with the cold cavity of the adjacent cylinder;
the working medium pressure detection unit is fixed on a detected cylinder of the Stirling engine and is used for measuring the working medium pressure in a heat cavity of each detected cylinder;
the crankshaft rotation angle measuring unit is fixed on the Stirling engine and used for measuring the rotation angle of the crankshaft corresponding to the measured cylinder.
Optionally, the crank angle measuring unit includes a rotating disc and an angle sensor, the rotating disc is mounted at an end portion of the crankshaft corresponding to the cylinder to be measured, the angle sensor is fixed on an end cover of a crankcase of the stirling engine and located on one side of the rotating disc, and the angle sensor is configured to sense rotation of the rotating disc and generate an angle signal when the rotating disc rotates.
Optionally, the corner sensor is photoelectric encoder, photoelectric encoder is fixed in on the end cover of crankcase and be located one side of rolling disc, the rolling disc is close to one side of photoelectric encoder is fixed with the dwang, the dwang with photoelectric encoder's rotor is connected, can drive when the dwang rotates photoelectric encoder's rotor rotates.
Optionally, the crank angle measuring unit further includes a static top dead center alignment assembly, the static top dead center alignment assembly includes a proximity sensor and an induction block, the induction block is fixed on the rotating disc, the proximity sensor is installed on the end cover of the crankcase and located on one side of a rotation path of the induction block, the proximity sensor is used for sensing the induction block, and when the induction block rotates to one side of the proximity sensor, the piston of the cylinder to be measured is located at the static top dead center of the piston of the cylinder to be measured.
Optionally, a first positioning module is arranged on the surface of the crankshaft, a second positioning module which can rotate around the first positioning module along with the rotation of the rotating disc is arranged on the rotating disc, when the first positioning module is in butt joint with the second positioning module, the phase of the induction block is the same as that of the piston of the cylinder to be measured, the position, opposite to the end of the crankshaft, on the end cover of the crankcase is the central position of the end cover of the crankcase, and the direction of the connecting line of the central position of the end cover of the crankcase and the proximity sensor is the same as the direction of the piston of the cylinder to be measured moving towards the top dead center of the piston.
Optionally, the rotating disc includes a balance disc and an adjusting disc, one side of the balance disc is fixed to the end of the crankshaft, the adjusting disc is fixed to the other side of the balance disc, and a balance gap for balancing the rotation of the rotating disc is formed in the circumferential direction of the balance disc.
Optionally, the balance disc is detachably connected to the adjustment disc, a first phase positioning hole is formed in the surface of the adjustment disc, a plurality of second phase positioning holes are formed in the circumferential direction of the balance disc at intervals, each second phase positioning hole corresponds to a phase of a piston of each cylinder, and when the first phase positioning hole is in butt joint with the second phase positioning hole corresponding to the piston of the cylinder to be measured, a phase of the induction block is the same as a phase of the piston of the cylinder to be measured.
Optionally, one side of the adjusting disc close to the balance disc is fixed with a positioning protrusion, one side of the balance disc close to the adjusting disc is provided with a positioning groove matched with the positioning protrusion, and the positioning protrusion is rotatably connected in the positioning groove.
Compared with the prior art, the Stirling engine cylinder pressure detection system provided by the invention has the beneficial effects that: the crank angle measuring unit is arranged on the Stirling engine, the working medium pressure detecting unit is fixed on a detected cylinder of the Stirling engine, and meanwhile, a connecting piece is arranged between cylinders of the engine and is a plugging piece with a communicating state or a communicating piece with a communicating state; when the pressure of a cylinder to be detected of the Stirling engine is detected, firstly, the connecting piece is switched to a blocking state, so that the working medium pressure detection unit measures the pressure of a hot cavity of the cylinder to be detected in the blocking state, meanwhile, the crankshaft angle measurement unit measures the angle of the crankshaft corresponding to the cylinder to be detected, and further the phase value of the crankshaft corresponding to the cylinder to be detected when the pressure of the hot cavity of the cylinder to be detected is at the maximum value can be obtained, wherein the crankshaft phase value is the crankshaft phase value of the dynamic top dead center of the piston of the cylinder to be detected; and then switching the connecting piece to a communication state, enabling each cylinder of the Stirling engine to operate in a normal state, enabling the working medium pressure detection unit to measure the pressure of the hot cavity of the detected cylinder in the normal state, enabling the crankshaft angle measurement unit to measure the angle of the crankshaft corresponding to the detected cylinder, obtaining a indicator diagram of the pressure of the hot cavity of the detected cylinder and the angle of the crankshaft, further obtaining a relation between the pressure of the hot cavity and the angle of the crankshaft by taking the phase of the piston dynamic top dead center of the detected cylinder as a reference, and finally realizing the detection of the pressure of the cylinder of the Stirling engine, thereby providing convenience for the performance analysis and the dynamic characteristic analysis of the Stirling engine.
In order to achieve the technical purpose, the technical scheme of the invention provides a method for detecting the cylinder pressure of a Stirling engine, which is executed by a Stirling engine cylinder pressure detection system and comprises the following steps:
s100: switching the connecting piece into a blocking piece to enable each cylinder of the Stirling engine to operate in a blocking state;
s200: acquiring the pressure of a hot cavity in the cylinder to be detected through the pressure detection unit, and acquiring a crank angle corresponding to the cylinder to be detected through the crank angle measurement unit to obtain a crank phase value of a dynamic top dead center corresponding to the maximum hot cavity pressure of the cylinder to be detected;
s300: switching the connecting piece into a communicating piece to enable each cylinder of the Stirling engine to operate in a normal state;
s400: acquiring the pressure of a hot cavity in the cylinder to be detected through the pressure detection unit, and acquiring a corner of the crankshaft corresponding to the cylinder to be detected through the crankshaft corner measurement unit so as to obtain hot cavity pressure values of the cylinder to be detected corresponding to each phase of the crankshaft when the cylinder to be detected works normally;
s500: and taking the crankshaft phase value of the dynamic top dead center as a base point to obtain an indicator diagram of the relation between the pressure of the hot cavity of the measured cylinder and the crank angle.
Optionally, in the step S400, when the rotating disc rotates, the proximity sensor senses a sensing block to obtain a crankshaft phase value corresponding to a maximum pressure of each cylinder when the cylinder to be measured normally operates.
Compared with the prior art, the method for detecting the cylinder pressure of the Stirling engine has the beneficial effects that: according to the cylinder pressure detection method, the working medium pressure detection unit is used for measuring the pressure of a hot cavity of a detected cylinder in a blocking state, the crankshaft corner measurement unit is used for measuring the corner of a crankshaft corresponding to the detected cylinder, and therefore the crankshaft phase value of the piston dynamic top dead center of the detected cylinder can be obtained; the working medium pressure detection unit is used for measuring the pressure of a hot cavity of the measured cylinder in a normal working state, the crankshaft angle measurement unit is used for measuring the angle of the crankshaft corresponding to the measured cylinder, an indicator diagram of the pressure of the hot cavity of the measured cylinder and the angle of the crankshaft is obtained, and then the relation between the pressure of the hot cavity and the angle of the crankshaft based on the phase of the dynamic top dead center of the piston of the measured cylinder is obtained, the detection of the pressure of the cylinder of the Stirling engine is finally realized, and convenience is provided for performance analysis and dynamic characteristic analysis of the Stirling engine.
Drawings
Fig. 1 is a schematic structural diagram of a cylinder pressure detection system of a stirling engine according to embodiment 1 of the present invention.
Fig. 2 is a schematic structural diagram of a working medium circulation unit of a stirling engine cylinder pressure detection system according to embodiment 1 of the present invention.
Fig. 3 is a schematic structural diagram of a crank angle measuring unit of a cylinder pressure detecting system for a stirling engine according to embodiment 1 of the present invention.
Fig. 4 is an exploded view of a crank angle measuring unit of the cylinder pressure detecting system for the stirling engine according to embodiment 1 of the present invention.
Fig. 5 is a schematic structural view of a crank angle measuring unit of a stirling engine cylinder pressure detecting system according to embodiment 1 of the present invention in an assembled state.
Fig. 6 is a side view of a stirling engine cylinder pressure detecting system according to embodiment 1 of the present invention in an assembled state of a crank angle measuring unit.
Fig. 7 is a cross-sectional view taken along line a-a of fig. 6.
Fig. 8 is a P-phi indicator diagram based on static tdc and dynamic tdc provided in embodiment 1 of the present invention.
Fig. 9 is a flowchart of a method for detecting cylinder pressure of a stirling engine according to embodiment 2 of the present invention.
Wherein, in the figures, the respective reference numerals:
10-11-12-cylinder connecting piece of Stirling engine
13-crankshaft 14-crankcase 15-output shaft
16-flywheel 20-crankshaft angle measuring unit 21-rotating disk
22-static top dead center alignment assembly 111-piston 112-thermal chamber
113-cold chamber 114-connecting rod 131-driving gear
132-first positioning module 141-end cover 151-driven gear
211-balance disc 212-adjusting disc 213-second positioning module
221-proximity sensor 222-sensing block 2111-equilibrium gap
2112 second phase positioning hole 2113 positioning groove 2121 rotating rod
2122 first phase positioning hole 2123 and positioning boss.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and do not limit the invention.
The invention provides a cylinder pressure detection system of a Stirling engine and a detection method thereof.
Example 1:
embodiment 1 of the present invention provides a stirling engine cylinder pressure detection system, as shown in fig. 1-2, including a stirling engine 10, a working medium pressure detection unit (not identified in the figure) and a crank angle measurement unit 20, a connection member 12 is disposed between cylinders 11 of the stirling engine 10, one end of the connection member 12 is communicated with a hot cavity 112 of each cylinder 11, the other end of the connection member 12 is communicated with a cold cavity 113 of an adjacent cylinder 11, the connection member 12 is a communication member with a communication state or a blocking member with a blocking state, when the connection member 12 is a communication member, the hot cavity 112 of each cylinder 11 is communicated with the cold cavity 113 of the adjacent cylinder 11, and when the connection member 12 is a blocking member, the hot cavity 112 of each cylinder 11 is disconnected from the cold cavity 113 of the adjacent cylinder 11; the working medium pressure detection unit is fixed on the cylinders to be detected and is used for measuring the working medium pressure in the hot cavity 112 of each cylinder to be detected; the crank angle measuring unit 20 is fixed to the stirling engine 10 and measures the angle of rotation of the crankshaft 13 corresponding to the cylinder to be measured.
In this embodiment, as shown in fig. 1 to 2, two working units are disposed inside the stirling engine 10, each working unit includes four cylinders 11, a piston 111 is disposed in each cylinder 11, the piston 111 is connected to a crankshaft 13 through a connecting rod 114, the piston 111 partitions upper and lower sides of the cylinder 11 into a hot chamber 112 and a cold chamber 113, the piston 111 can reciprocate in the cylinder 11 to drive the crankshaft 13 to rotate, the crankshaft 13 of the stirling engine 10 is disposed in a crankcase 14, an output shaft 15 of the engine is disposed parallel to the crankshaft 13, a flywheel 16 is mounted at an end of the output shaft 15, a driving gear 131 is fixed on the crankshaft 13, a driven gear 151 engaged with the driving gear 131 is fixed on the output shaft 15, and the crankshaft 13 drives the output shaft 15 to rotate through the driving gear 131 and the driven gear 151, thereby driving the flywheel 16 to rotate.
Specifically, a crank angle measuring unit 20 is arranged on the Stirling engine 10, a working medium pressure detecting unit is fixed on a detected cylinder of the Stirling engine 10, and a connecting piece 12 with a communication state and a blocking state is arranged between cylinders 11 of the engine; when the pressure of a cylinder to be detected of the Stirling engine 10 is detected, firstly, the connecting piece 12 is switched to a blocking state, the Stirling engine 10 is dragged backwards by the motor, each cylinder 11 of the Stirling engine 10 operates in the blocking state, the working medium pressure detection unit measures the pressure P of the hot cavity 112 of the cylinder to be detected in the blocking state, meanwhile, the crankshaft rotation angle measurement unit 20 measures the rotation angle phi of the crankshaft 13 corresponding to the cylinder to be detected, a pure compression line of the relation between the pressure of the hot cavity 112 and the rotation angle phi of the crankshaft 13 in the blocking state of the cylinder to be detected is obtained, the rotation angle corresponding to the crankshaft 13 under the maximum pressure of the hot cavity 112 of the cylinder to be detected can be reflected on the pure compression line, and the crankshaft phase value 13 is the crankshaft phase value of the dynamic top dead center of the piston 111 of the cylinder to be detected; and then the connecting piece 12 is switched to a communicating state, each cylinder 11 of the Stirling engine 10 operates in a normal state, the working medium pressure detection unit is used for measuring the pressure P of the hot cavity 112 of the measured cylinder in the normal state, the crankshaft rotation angle measurement unit 20 is used for measuring the rotation angle phi of the crankshaft 13 corresponding to the measured cylinder, a P-phi indicator diagram of the pressure P of the hot cavity 112 of the measured cylinder and the rotation angle phi of the crankshaft 13 is obtained, and further the relation between the pressure P of the hot cavity 112 and the rotation angle phi of the crankshaft 13 by taking the phase of the dynamic top dead center of the piston 111 of the measured cylinder as the reference is obtained, so that the pressure of the cylinder 11 of the Stirling engine 10 is finally detected, and convenience is provided for performance analysis and dynamic characteristic analysis of the Stirling engine 10.
In this embodiment, the connecting member 12 is a plugging member or a cooler of the stirling engine 10, and when the state of the connecting member 12 is switched, only the plugging member and the cooler need to be switched and installed, wherein two separation chambers separated by a partition plate are arranged inside the plugging member, when the plugging member is installed, one of the separation chambers is communicated with the hot chamber 112 of each cylinder 11, the other separation chamber is communicated with the cold chamber 113 of the adjacent cylinder 11, and the hot chamber 112 and the cold chamber 113 of the two adjacent cylinders 11 are separated by the partition plate, so that the hot chamber 112 and the cold chamber 113 of the two adjacent cylinders 11 are finally plugged; the cooler is an original cooler of the Stirling engine 10, and when the cooler is installed between the cylinders 11, the hot cavity 112 and the cold cavity 113 of two adjacent cylinders 11 are communicated.
In this embodiment, the thermal cavity 112 of each cylinder 11 is connected to the combustion chamber of the stirling engine 10, and each cylinder 11 and each connecting member 12 constitute a working medium circulation unit of the stirling engine 10; taking the four-cylinder stirling engine 10 as an example, when the connecting piece 12 is a plugging device, the working medium circulation unit is in a plugging state, the four plugging devices separate the working medium circulation unit and form four closed hot cavities 112 and four closed cold cavities 113, the maximum pressures of the four hot cavities 112 and the four cold cavities 113 are the same, and since the working medium circulation unit in the plugging state cannot adjust the pressure of the hot cavity 112 and can only balance by the pumping action of the ring of the piston 111, the problems of high pressure ratio and severe vibration are likely to be caused, therefore, the pure compression line detection should be performed under the low working condition (the highest working medium pressure is not more than 5MPa, and the rotating speed is not more than 1000 r/min) of the stirling engine 10. Meanwhile, as the cylinder sleeve water cavity is not cooled by cooling water, the working condition of the working of the 111 ring of the piston is severe, and the time of single test is ensured to be within 3 min. The cold chamber 113 can be cooled by cooling water to ensure that the temperature of the working medium in the cold chamber 113 is low. If the temperature of the thermal chamber 112 is high, the fan is used for cooling.
After the working medium circulation unit reaches a preset stable state, the Stirling engine 10 is dragged backwards through the motor, data are recorded and stored (the running time of the engine is guaranteed within 3 min), and a pure compression line of the Stirling engine 10 is obtained.
In this embodiment, the working medium pressure detection unit is a pressure sensor.
It is understood that the crank angle measuring unit may calculate the rotation angle of the crankshaft 13 by measuring the rotation angle of the flywheel 16 and then calculating the rotation angle of the crankshaft 13 based on the gear ratio of the driving gear 131 on the crankshaft 13 and the driven gear 151 of the output shaft 15. Or by directly measuring the rotational angle of the crankshaft 13.
Alternatively, as shown in fig. 3 to 7, the crank angle measuring unit 20 includes a rotary disc 21 and an angle sensor (not shown), the rotary disc 21 is mounted at an end portion of the crankshaft 13 corresponding to the cylinder to be measured, the angle sensor is fixed to an end cover 141 of the crankcase 14 of the stirling engine 10 and is located at one side of the rotary disc 21, and the angle sensor is configured to sense rotation of the rotary disc 21 and generate an angle signal when the rotary disc 21 rotates. Specifically, by providing the rotating disk 21 at the end of the crankshaft 13 and providing the rotation angle sensor for measuring the rotation angle of the rotating disk 21 on the end cover 141 of the crankcase 14, accurate measurement of the rotation angle of the crankshaft 13 corresponding to the measured rod body can be achieved.
In this embodiment, the rotation angle sensor may be a hall sensor, the hall sensor is located on one side of the protruding teeth by arranging a plurality of protruding teeth at regular intervals on the periphery of the rotating disc 21, and the hall sensor senses the protruding teeth to obtain the rotation angle of the rotating disc 21. The rotation angle sensor can also be a photoelectric encoder, and a rotor in the photoelectric encoder is driven to rotate when the rotary disc rotates, so that the rotation angle of the rotary disc 21 is obtained.
Optionally, as shown in fig. 3 to 7, the rotation angle sensor is a photoelectric encoder, the photoelectric encoder is fixed on the end cover 141 of the crankcase 14 and located on one side of the rotating disc 21, a rotating rod 2121 is fixed on one side of the rotating disc 21 close to the photoelectric encoder, the rotating rod 2121 is connected to a rotor of the photoelectric encoder, and the rotating rod 2121 can drive the rotor of the photoelectric encoder to rotate when rotating.
Specifically, when the rotating disc 21 rotates, the rotating rod 2121 is driven to rotate, when the rotating rod 2121 rotates, the rotor of the photoelectric encoder is driven to rotate, when the rotor of the photoelectric encoder rotates, the number of square wave signals generated by the photoelectric encoder when the rotating rod 2121 rotates for one cycle is sent to the signal acquisition system, the number of square wave signals generated by the photoelectric encoder when the rotating rod 2121 rotates for one cycle is set as n, when the rotating rod 2121 rotates for 360/n degrees (indicated by a letter a), the photoelectric encoder generates one square wave signal, the n square wave signals are sequenced by natural numbers 1, 2, 3, 1.. and n, the maximum value of the pressure of the thermal cavity 112 in the blocking state is obtained by a pure compression line of the relationship between the pressure of the thermal cavity 112 in the blocking state of the cylinder and the rotation angle of the crankshaft 13, and the serial number of the square wave signal corresponding to the maximum pressure of the thermal cavity 112 is obtained by the pure compression line, multiplying the serial number by a to obtain a crankshaft 13 phase position alpha corresponding to the dynamic top dead center of the tested cylinder of the crankshaft 13, and then taking the crankshaft 13 phase position alpha corresponding to the dynamic top dead center of the tested cylinder 11 as a base point to prepare a P-phi indicator diagram of the pressure P of the hot cavity 112 of the tested cylinder and the rotation angle phi of the crankshaft 13 shown in the figure 8, so as to facilitate performance analysis and dynamic characteristic analysis of the Stirling engine 10.
Optionally, as shown in fig. 3 to 7, the crank angle measuring unit 20 further includes a static top dead center alignment assembly 22, the static top dead center alignment assembly 22 includes a proximity sensor 221 and a sensing block 222, the sensing block 222 is fixed on the rotating disc 21, the proximity sensor 221 is mounted on the end cover 141 of the crankcase 14 and located on one side of a rotation path of the sensing block 222, the proximity sensor 221 is configured to sense the sensing block 222, and when the sensing block 222 rotates to one side of the proximity sensor 221, the piston 111 of the cylinder to be measured is located at the static top dead center of the piston 111 of the cylinder to be measured.
Specifically, when the proximity sensor 221 senses that the sensing block 222 rotates to one side of the proximity sensor 221, the proximity sensor 221 generates a sensing signal, a serial number of a crankshaft 13 rotation angle corresponding to a square wave signal generated by the proximity sensor 221 is found, the serial number is multiplied by a to obtain a crankshaft 13 phase β corresponding to a static top dead center of the cylinder to be measured, and an indicator diagram of the pressure of the cylinder thermal cavity 112 to be measured and the rotation angle of the crankshaft 13, which is shown in fig. 8, is prepared based on the crankshaft 13 phase β corresponding to the static top dead center of the cylinder 11 to be measured, so as to study the combustion characteristics of the stirling engine 10.
By combining the dynamic upper dead center positioning and the static upper dead center positioning, the cylinder pressure test can be performed according to different types and structures of the Stirling engine 10, and the phase difference between the static upper dead center and the dynamic upper dead center can also be obtained at the same time, so that the signal acquisition precision is improved, high-precision equal-crank shaft 13-corner signals are directly generated, the signal processing difficulty is greatly reduced, the high-precision Stirling engine 10 cylinder pressure signals are finally obtained, and good technical support is provided for performance analysis and dynamic characteristic analysis of the Stirling engine 10.
In the present embodiment, the proximity sensor 221 is a hall sensor.
Optionally, as shown in fig. 3 to 7, a first positioning module 132 is disposed on a surface of the crankshaft 13, a second positioning module 213 that can rotate around the first positioning module 132 along with rotation of the rotating disc 21 is disposed on the rotating disc 21, when the first positioning module 132 is in butt joint with the second positioning module 213, a phase of the sensing block 222 is the same as a phase of the piston 111 of the cylinder to be measured, a position of the end cover 141 of the crankcase 14 that is opposite to the end of the crankshaft 13 is a central position of the end cover 141 of the crankcase 14, and a direction of a connection line between the central position of the end cover 141 of the crankcase 14 and the proximity sensor 221 is the same as a direction of the piston 111 of the cylinder to be measured moving toward a top dead center of the piston 111.
Specifically, when the rotating disc 21 is installed, the first positioning module 132 is abutted to the second positioning module 213, that is, the phase of the sensing block 222 is the same as the phase of the piston 111 of the cylinder to be measured, and meanwhile, since the connection line between the proximity sensor 221 and the central portion of the end cover 141 of the crankcase 14 is the same as the direction of the piston 111 of the cylinder to be measured moving toward the top dead center of the piston 111, when the proximity sensor 221 senses the sensing block 222, the rotation angle of the crankshaft 13 corresponding to the sensing signal generated by the proximity sensor 221 is the rotation angle of the crankshaft 13 when the piston 111 of the cylinder to be measured moves to the top of the cylinder to be measured (i.e., the static top dead center), thereby achieving the measurement of the rotation angle of the crankshaft 13 corresponding to the static top dead center of the cylinder to be measured.
In this embodiment, as shown in fig. 7, the first positioning module 132 and the second positioning module 213 are both positioning pin holes, and when the rotating disc 21 is mounted, the positioning pin holes on the rotating disc 21 are butted with the positioning pin holes on the crankshaft 13, so that the phase of the sensing block 222 can be the same as the phase of the piston 111 of the cylinder to be measured, and then the rotating disc 21 can be fixed by the positioning pins.
In this embodiment, the positioning pin holes on the crankshaft 13 and the position of the sensing block 222 on the rotating disc 21 are determined by program calculation.
Optionally, as shown in fig. 3 to 7, the rotating disc 21 includes a balance disc 211 and an adjusting disc 212, one side of the balance disc 211 is fixed to the end of the crankshaft 13, the adjusting disc 212 is fixed to the other side of the balance disc 211, and a balance notch 2111 for balancing the rotation of the rotating disc 21 is provided in the circumferential direction of the balance disc 211. Specifically, the balance notch 2111 can effectively balance the centrifugal moment of inertia and the reciprocating moment of inertia of the transmission mechanism.
In this embodiment, as shown in fig. 4 and 7, a positioning protrusion 2123 is fixed to a central portion of one surface of the adjusting plate 212 close to the balance plate 211, a positioning groove 2113 adapted to the positioning protrusion 2123 is provided on one surface of the balance plate 211 close to the adjusting plate 212, and the positioning protrusion 2123 is rotatably connected in the positioning groove 2113. The positioning protrusion 2123 and the positioning groove 2113 are arranged to effectively provide positioning for the installation of the adjustment disc 212, and facilitate the rotation of the adjustment disc 212.
Optionally, as shown in fig. 3 to 5, the balance disc 211 is detachably connected to the adjustment disc 212, a first phase positioning hole 2122 is disposed on a surface of the adjustment disc 212, a plurality of second phase positioning holes 2112 are disposed at intervals in a circumferential direction of the balance disc 211, each second phase positioning hole 2112 corresponds to a phase of the piston 111 of each cylinder 11, and when the first phase positioning hole 2122 is in butt joint with the second phase positioning hole 2112 corresponding to the piston 111 of the cylinder to be measured, a phase of the sensing block 222 is the same as a phase of the piston 111 of the cylinder to be measured.
Specifically, after the balance disc 211 is fixed to the end of the crankshaft 13, the first phase positioning hole 2122 can be butted with the second phase positioning hole 2112 corresponding to the piston 111 of the cylinder to be measured by rotating the adjusting disc 212, and further, the first phase positioning hole 2122 can be butted with the second phase positioning hole 2112 corresponding to the piston 111 of the cylinder to be measured, and by rotating the adjusting disc 212, not only can the adjusting disc 212 be quickly positioned, but also when measuring the static top dead center phase of another cylinder, the phase of the sensing block 222 can be the same as the phase of the piston in the cylinder by only rotating the adjusting disc 212 to butt the first phase positioning hole 2122 with the second phase positioning hole 2112 corresponding to the cylinder, so that the crank angle measuring unit 20 is adapted to detect the static top dead centers of different pistons.
In this embodiment, as shown in fig. 3 to 4, the number of the first phase positioning holes 2122 is 6, when the 6 first phase positioning holes 2122 are abutted to the 6 second phase positioning holes 2112 corresponding to the piston 111 of the cylinder to be measured in all the second phase positioning holes 2112 on the balance disc 211, the phase of the induction block 222 is the same as the phase of the piston 111 of the cylinder to be measured, and the adjusted adjustment disc 212 is fixed through the 6 first phase positioning holes 2122. The balance disc 211 and the adjustment disc 212 can be fixed by the 6 first phase positioning holes 2122.
Example 2:
embodiment 2 of the present invention provides a stirling engine cylinder pressure detection method, which is performed by a stirling engine cylinder pressure detection system, and includes the following steps:
s100: switching the connecting piece 12 into a blocking piece to enable each cylinder 11 of the Stirling engine 10 to operate in a blocking state;
s200: acquiring the pressure of the thermal cavity in the cylinder to be detected through the pressure detection unit, and acquiring the rotation angle of the crankshaft corresponding to the cylinder to be detected through the crankshaft rotation angle measurement unit 20 to obtain a crankshaft phase value of a dynamic top dead center corresponding to the maximum thermal cavity pressure of the cylinder to be detected;
s300: switching the connecting member 12 to a communicating member to allow each cylinder 11 of the stirling engine 10 to operate in a normal state;
s400: acquiring the pressure of a hot cavity in the cylinder to be measured through the pressure detection unit, and acquiring a corner of the crankshaft corresponding to the cylinder to be measured through the crankshaft corner measurement unit 20, so as to obtain hot cavity pressure values of the cylinder to be measured corresponding to each phase of the crankshaft when the cylinder to be measured normally works;
s500: and taking the crankshaft phase value of the dynamic top dead center as a base point to obtain an indicator diagram of the relation between the pressure of the hot cavity of the measured cylinder and the crankshaft rotation angle.
Specifically, the cylinder pressure detection method measures the pressure of a hot cavity 112 of a detected cylinder in a blocking state through a working medium pressure detection unit, and measures a corner of a crankshaft 13 corresponding to the detected cylinder through a crankshaft corner measurement unit 20, so as to obtain a crankshaft phase value of a dynamic top dead center of a piston 111 of the detected cylinder; the working medium pressure detection unit is used for measuring the pressure of the thermal cavity 112 of the measured cylinder in a normal working state, the crankshaft angle measurement unit 20 is used for measuring the angle of the crankshaft 13 corresponding to the measured cylinder, an indicator diagram of the pressure of the thermal cavity 112 of the measured cylinder and the angle of the crankshaft 13 is obtained, further, the relation between the pressure of the thermal cavity 112 and the angle of the crankshaft 13 with the phase position of the dynamic top dead center of the piston 111 of the measured cylinder as the reference is obtained, the detection of the pressure of the cylinder 11 of the Stirling engine 10 is finally realized, and convenience is provided for performance analysis and dynamic characteristic analysis of the Stirling engine 10.
Alternatively, in step S400, when the rotating disc 21 rotates, the proximity sensor 221 senses the sensing block 222 to obtain the phase value of the crankshaft 13 corresponding to the maximum pressure of each cylinder 11 when the cylinder to be measured normally operates.
In this embodiment, when the rotating disc 21 is installed, the first positioning module 132 is abutted with the second positioning module 213, and the first phase positioning hole 2122 is abutted with the second phase positioning hole 2112 corresponding to the piston 111 of the cylinder to be tested, so that the phase of the sensing block 222 is the same as the phase of the piston 111 of the cylinder to be tested.
The above-described embodiments of the present invention should not be construed as limiting the scope of the present invention. Any other corresponding changes and modifications made according to the technical idea of the present invention should be included in the protection scope of the claims of the present invention.
Claims (10)
1. A Stirling engine cylinder pressure detection system comprises a Stirling engine and is characterized by further comprising a working medium pressure detection unit and a crankshaft angle measurement unit, wherein a connecting piece is arranged between cylinders of the Stirling engine, one end of the connecting piece is communicated with a hot cavity of each cylinder, the other end of the connecting piece is communicated with a cold cavity of an adjacent cylinder, the connecting piece is a blocking piece with a communicated state or a communicating piece with a communicated state, when the connecting piece is a blocking piece, the hot cavity of each cylinder is disconnected with the cold cavity of the adjacent cylinder, and when the connecting piece is a communicating piece, the hot cavity of each cylinder is communicated with the cold cavity of the adjacent cylinder;
the working medium pressure detection unit is fixed on a detected cylinder of the Stirling engine and is used for measuring the working medium pressure in a heat cavity of each detected cylinder;
the crankshaft rotation angle measuring unit is fixed on the Stirling engine and used for measuring the rotation angle of the crankshaft corresponding to the measured cylinder.
2. A stirling engine cylinder pressure sensing system according to claim 1, wherein the crank angle measuring unit includes a rotary plate mounted to an end of the crankshaft corresponding to the cylinder to be sensed, and an angle sensor fixed to an end cap of a crankcase of the stirling engine on a side of the rotary plate, the angle sensor being adapted to sense rotation of the rotary plate and generate an angle signal when the rotary plate rotates.
3. A Stirling engine cylinder pressure detecting system according to claim 2, wherein the rotation angle sensor is a photoelectric encoder, the photoelectric encoder is fixed to an end cover of the crankcase and located on one side of the rotary disc, a rotary rod is fixed to one side of the rotary disc close to the photoelectric encoder, the rotary rod is connected with a rotor of the photoelectric encoder, and the rotary rod drives the rotor of the photoelectric encoder to rotate when rotating.
4. A stirling engine cylinder pressure sensing system according to claim 2, wherein the crank angle measuring unit further comprises a static top dead center alignment assembly, the static top dead center alignment assembly comprising a proximity sensor and a sensing block, the sensing block being fixed to the rotating disc, the proximity sensor being mounted to the end cap of the crankcase and located on one side of a rotation path of the sensing block, the proximity sensor being configured to sense the sensing block, the piston of the cylinder being measured being at the static top dead center of the piston of the cylinder being measured when the sensing block is rotated to one side of the proximity sensor.
5. A Stirling engine cylinder pressure detecting system according to claim 4, wherein a first positioning module is arranged on a surface of the crankshaft, a second positioning module which can rotate around the first positioning module along with rotation of the rotating disc is arranged on the rotating disc, when the first positioning module and the second positioning module are in butt joint, a phase of the sensing block is the same as a phase of a piston of the cylinder to be detected, a position of an end cover of the crankcase, which is opposite to an end of the crankshaft, is a central position of the end cover of the crankcase, and a connecting line direction of the central position of the end cover of the crankcase and the proximity sensor is the same as a direction when the piston of the cylinder to be detected moves towards a top dead center of the piston.
6. A Stirling engine cylinder pressure detecting system according to claim 4, wherein the rotating disc comprises a balance disc and an adjusting disc, one side of the balance disc is fixed to an end of the crankshaft, the adjusting disc is fixed to the other side of the balance disc, and a balance notch for balancing rotation of the rotating disc is provided in the circumferential direction of the balance disc.
7. A Stirling engine cylinder pressure detecting system according to claim 6, wherein the balance disc is detachably connected to the adjusting disc, a first phase positioning hole is formed in the surface of the adjusting disc, a plurality of second phase positioning holes are formed in the balance disc in the circumferential direction at intervals, each second phase positioning hole corresponds to a phase of a piston of each cylinder, and when the first phase positioning hole is in butt joint with the second phase positioning hole corresponding to the piston of the cylinder to be detected, the phase of the sensing block is the same as the phase of the piston of the cylinder to be detected.
8. A Stirling engine cylinder pressure detecting system according to claim 6, wherein a positioning protrusion is fixed to one surface of the adjusting plate close to the balance plate, a positioning groove matched with the positioning protrusion is formed in one surface of the balance plate close to the adjusting plate, and the positioning protrusion is rotatably connected in the positioning groove.
9. A method for detecting the cylinder pressure of a Stirling engine, which is performed by the system for detecting the cylinder pressure of a Stirling engine according to any one of claims 4 to 8, comprising the steps of:
s100: switching the connecting piece into a blocking piece to enable each cylinder of the Stirling engine to operate in a blocking state;
s200: acquiring the pressure of a hot cavity in the cylinder to be detected through the pressure detection unit, and acquiring a crank angle corresponding to the cylinder to be detected through the crank angle measurement unit to obtain a crank phase value of a dynamic top dead center corresponding to the maximum hot cavity pressure of the cylinder to be detected;
s300: switching the connecting piece into a communicating piece to enable each cylinder of the Stirling engine to operate in a normal state;
s400: acquiring the pressure of a hot cavity in the cylinder to be detected through the pressure detection unit, and acquiring a corner of the crankshaft corresponding to the cylinder to be detected through the crankshaft corner measurement unit so as to obtain hot cavity pressure values of the cylinder to be detected corresponding to each phase of the crankshaft when the cylinder to be detected works normally;
s500: and taking the crankshaft phase value of the dynamic top dead center as a base point to obtain an indicator diagram of the relation between the pressure of the hot cavity of the measured cylinder and the crank angle.
10. A method for detecting cylinder pressure of a stirling engine in accordance with claim 9, wherein in step S400, the proximity sensor senses a sensing block while the rotary plate rotates, so as to obtain a crank phase value corresponding to a maximum pressure of each cylinder when the cylinder to be detected is operating normally.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210421269.1A CN114526916B (en) | 2022-04-21 | 2022-04-21 | Stirling engine cylinder pressure detection system and detection method thereof |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210421269.1A CN114526916B (en) | 2022-04-21 | 2022-04-21 | Stirling engine cylinder pressure detection system and detection method thereof |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN114526916A true CN114526916A (en) | 2022-05-24 |
| CN114526916B CN114526916B (en) | 2022-07-26 |
Family
ID=81627951
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210421269.1A Active CN114526916B (en) | 2022-04-21 | 2022-04-21 | Stirling engine cylinder pressure detection system and detection method thereof |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN114526916B (en) |
Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4111041A (en) * | 1977-09-29 | 1978-09-05 | The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Indicated mean-effective pressure instrument |
| US4253303A (en) * | 1979-10-01 | 1981-03-03 | Liljequist Jon L | Engines, and particularly those incorporating the Stirling cycle |
| US5219398A (en) * | 1990-08-10 | 1993-06-15 | Yamaha Hatsudoki Kabushiki Kaisha | Control device for internal combustion engine |
| CN101738211A (en) * | 2008-11-21 | 2010-06-16 | 比亚迪股份有限公司 | Device and method for measuring rotation angle of engine crankshaft |
| JP2013024236A (en) * | 2011-10-14 | 2013-02-04 | Akira Watanabe | Stirling engine |
| CN104314688A (en) * | 2014-08-13 | 2015-01-28 | 吉林大学 | Device and method for judging rotation phase position and real-time position of engine crankshaft |
| US20160032852A1 (en) * | 2014-07-29 | 2016-02-04 | Freescale Semiconductor, Inc. | Method of calibrating a crank angle of a combustion engine |
-
2022
- 2022-04-21 CN CN202210421269.1A patent/CN114526916B/en active Active
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4111041A (en) * | 1977-09-29 | 1978-09-05 | The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Indicated mean-effective pressure instrument |
| US4253303A (en) * | 1979-10-01 | 1981-03-03 | Liljequist Jon L | Engines, and particularly those incorporating the Stirling cycle |
| US5219398A (en) * | 1990-08-10 | 1993-06-15 | Yamaha Hatsudoki Kabushiki Kaisha | Control device for internal combustion engine |
| CN101738211A (en) * | 2008-11-21 | 2010-06-16 | 比亚迪股份有限公司 | Device and method for measuring rotation angle of engine crankshaft |
| JP2013024236A (en) * | 2011-10-14 | 2013-02-04 | Akira Watanabe | Stirling engine |
| US20160032852A1 (en) * | 2014-07-29 | 2016-02-04 | Freescale Semiconductor, Inc. | Method of calibrating a crank angle of a combustion engine |
| CN104314688A (en) * | 2014-08-13 | 2015-01-28 | 吉林大学 | Device and method for judging rotation phase position and real-time position of engine crankshaft |
Non-Patent Citations (5)
| Title |
|---|
| FIRSTNER, S.; FURSTNER, I.: "Resonant Stirling engines", 《PROCEEDINGS OF THE 2011 IEEE 3RD INTERNATIONAL SYMPOSIUM ON EXPLOITATION OF RENEWABLE ENERGY SOURCES (EXPRES 2011)》 * |
| 孙思聪: "热气机振动特性计算与试验研究", 《中国优秀硕士学位论文全文数据库（电子期刊）工程科技II辑》 * |
| 崔海龙: "多缸发动机气缸压力采集与燃烧分析***的研究", 《中国优秀硕士学位论文全文数据库（电子期刊）工程科技II辑》 * |
| 张鑫: "斯特林发动机的性能模拟及其热电联产***设计", 《中国优秀硕士学位论文全文数据库（电子期刊）工程科技II辑》 * |
| 袁泉: "柴油机性能监测***的开发与试验研究", 《中国优秀硕士学位论文全文数据库（电子期刊）工程科技II辑》 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN114526916B (en) | 2022-07-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| KR100255218B1 (en) | Method and apparatus for testing engines | |
| Varbanets et al. | Improvement of diagnosing methods of the diesel engine functioning under operating conditions | |
| JP2016183671A (en) | Systems and methods for locating engine event | |
| US20170175661A1 (en) | Real time detection and diagnosis of change in peak firing pressure | |
| JP2016125494A (en) | System and method for regulating exhaust gas recirculation in engine | |
| US20160312716A1 (en) | Knock sensor systems and methods for detection of component conditions | |
| BR102016002606B1 (en) | DIAGNOSIS METHOD AND SYSTEM OF A DETONATION SENSOR AND NON-TRANSITORY COMPUTER-READable MEDIUM | |
| CN113431680A (en) | Full-period acquisition and instantaneous speed calculation method of engine monitoring signals based on tooth pulse of tooth-lacking fluted disc | |
| CN114526916B (en) | Stirling engine cylinder pressure detection system and detection method thereof | |
| Mohammed et al. | Performance and combustion characteristics of a novel crank-rocker engine | |
| US8695408B2 (en) | Device and method for measuring engine torque and control program | |
| RU2454643C1 (en) | Method of defining ice power losses | |
| US20200332733A1 (en) | System and method for estimating engine performance | |
| CN107701320B (en) | Method and system for estimating combustion state in cylinder of multi-cylinder engine | |
| JP2001082238A (en) | Method for deciding top dead center phase of reciprocating compression engine | |
| KR20210005823A (en) | Misfiring cylinder detection method and device for reciprocating internal combustion engine using torsional vibration signal | |
| JP2013032726A (en) | Abnormality diagnostic device for internal combustion engine | |
| JPH0259941B2 (en) | ||
| EP3344969B1 (en) | Method for operating a piston engine and arrangement for detecting failure of a head gasket | |
| KR100351998B1 (en) | Measurement apparatus for piston ring | |
| Pagonis et al. | Low Cost Measurement System for the Precise Monitoring of the Instantaneous Rotational Speed of an Internal Combustion Engine | |
| RU2785419C1 (en) | Method for estimating the power of mechanical losses of an internal combustion engine | |
| FUJIMOTO et al. | Measurement of cylinder bore deformation by means of a turning piston with a gap sensor during engine operation | |
| Zhang et al. | Diagnosis of the working unevenness of each cylinder by the transient crankshaft speed | |
| CN201653338U (en) | Deviation detection device of dead center position on diesel 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 |