JPS6016736Y2 - Rotary piston engine rotor cooling system - Google Patents

Description

[Detailed Description of the Invention] (Industrial Application Field) The present invention relates to a rotor cooling device in a rotary piston engine.

(Prior art) Generally, in a rotary piston engine, the air-fuel mixture is combusted in a flat combustion chamber with a large surface area to volume ratio, that is, a large S/V ratio.
In order to reduce the amount of unburned precepts, it is necessary to keep the rotor temperature as high as possible by cooling the rotor to the minimum necessary.

Therefore, conventionally, in the oil supply passage formed on the eccentric shaft,
A control valve is provided, which is composed of a valve body that opens due to the centrifugal force generated by the rotation of the eccentric shaft and a spring that biases the valve body in the valve closing direction, and that opens and closes in response to increases and decreases in the centrifugal force. By controlling the amount of oil supplied to the inside of the rotor, the oil supply to the rotor is stopped when the engine is running at low speeds, and when the engine is running at high speeds with a high heat load, oil is supplied to the inside of the rotor to cool the rotor. Various types of rotor cooling devices have been proposed (see, for example, Japanese Patent Application No. 53-69186 filed by the applicant of the present invention).

(Problem that the invention aims to solve) However, in the above-mentioned conventional method, no consideration is given to the warm-up state of the engine, so the oil supply amount is adjusted to the demand after warm-up when the rotor temperature is high. If set to this value, more oil than the required amount will be supplied during warm-up when the rotor temperature is low, causing the rotor to become overcooled.If set to the opposite value, there will be a problem that oil will be insufficient after warm-up and the rotor will become overheated. be.

In addition, in the above-mentioned conventional valve, the valve opening timing is set by the centrifugal force and oil pressure acting on the valve body, so the timing changes due to changes in the viscous resistance of the oil, and when the engine is at low temperature. In this case, the valve opening timing is advanced and the rotor becomes overcooled.

The present invention has been made in view of the above points, and is a rotor cooling system for a rotary piston engine that allows the rotor to be appropriately cooled according to the operating state of the engine, that is, according to the warm-up state and engine speed of the engine. It is an object of the present invention to provide a device and thus to overcome the above-mentioned drawbacks of the prior art.

(Means for Solving the Problems) Therefore, in the present invention, the engine rotation speed, that is, the rotation speed of the eccentric shaft, depends on the centrifugal force acting on the valve body of the control valve provided in the oil supply passage of the eccentric shaft. In addition, this method takes advantage of the fact that the warm-up state of the engine corresponds approximately to the temperature of the oil discharged from the rotor.

Specifically, as described above, the control valve is composed of a valve body that opens due to centrifugal force caused by rotation of an eccentric shaft and a spring that biases the valve body in the valve closing direction, and opens and closes in response to increases and decreases in the centrifugal force. A first pressure-receiving surface that applies hydraulic pressure from an oil supply passage to press the valve element in the valve-opening direction and a second pressure-receiving surface that presses the valve element in the valve-closing direction are formed on the valve element. A temperature-sensitive control valve is provided in the oil passage that guides the oil pressure in the passage to the second pressure-receiving surface, and when the oil temperature is below a set value, the temperature-sensitive control valve opens the oil passage, and when the oil temperature is above the set value. The oil passage is closed using a temperature-sensitive control valve.

(Function) As a result, in the present invention, when the engine is warmed up,
The opening operation of the temperature-sensitive control valve opens the oil passage that guides the oil pressure in the oil supply passage to the second pressure-receiving surface, and the oil pressure acts on both the first and second pressure-receiving surfaces and cancels each other out, thereby controlling the oil pressure. Only centrifugal force acts as the force in the valve opening direction on the valve body of the valve, and as this centrifugal force increases, that is, the engine speed increases, the control valve opens and the rotor is cooled without overcooling.

On the other hand, after the engine has warmed up, the oil passage is closed by the closing operation of the temperature-sensitive control valve, and the oil pressure is guided only to the first pressure receiving surface. As a result, the opening timing of the control valve is advanced, and as the oil pressure increases and the centrifugal force increases, the opening area is determined only by the centrifugal force. larger than the opening area,
The rotor can be properly cooled after warming up without causing overheating.

(Example) Hereinafter, an example of the present invention will be described in detail based on the drawings.

In FIG. 1, 1 is a casing composed of a rotor housing 2 and side housings 3, 3 disposed on both sides of the rotor housing, 4 is a polygonal rotor supported on an eccentric shaft 5, and rotates planetarily within the casing 1; Reference numeral 6 is a rotor gear provided on one side of the rotor 4, and 7 is a fixed gear fixed to the side housing 3. These provide continuous suction, compression, explosion, expansion, and It consists of a rotary piston engine that repeats each exhaust stroke.

On the other hand, 8 is an oil supply passage provided at the center of the eccentric shaft 5 for pumping oil from an oil pump 9 driven by the engine, and 10 is an oil supply passage that branches from the oil supply passage 8 on the side opposite to the rotor gear and is connected to the hollow part of the rotor 4. The branch passage 10 opens toward the chamber 4a, and a control valve 11 is provided in the branch passage 10 to control the timing and amount of oil supplied to the hollow chamber 4a.

As shown in FIGS. 2 and 3, the control valve 11 has a cylindrical case 11b having a valve hole 11a on the side surface, and is slidably fitted into the case 11b so as to open and close the valve hole 11a. The valve body 11c is made up of a valve body 11c which is opened by the centrifugal force generated by the rotation of the eccentric shaft 5, and a spring Ild which biases the valve body 11c in the valve closing direction. First and second pressure-receiving surfaces 11e and llf facing each other are formed.

The first pressure receiving surface 11e communicates with the oil supply passage 8 via the branch passage 10, and applies the hydraulic pressure of the oil supply passage 8 to press the valve body 11c in the valve opening direction.
1f is an oil passage 11g formed in the case Ilb.
The hydraulic pressure of the oil supply passage 8 is applied to the oil supply passage 8 via the valve body 11c to press the valve body 11c in the valve closing direction.

Reference numeral 11h denotes an oil introduction hole formed in the case Ilb, which is configured to guide oil discharged from the rotor hollow chamber 4a and having a temperature corresponding to the rotor temperature to a temperature-sensitive control valve 12, which will be described later.

Furthermore, a temperature-sensitive control valve 12 that detects the oil temperature and opens and closes is interposed in the oil passage 11g.

The temperature-sensitive control valve 12 includes a thermopellet 12a that contracts and expands depending on the oil temperature, and a valve body 12b that opens and closes the oil passage 11g in conjunction with the contraction and expansion of the thermopellet 12a. When the value is below the set value, the valve element 12b is opened by the contraction of the thermopellet 12a to open the oil passage 11g, and the second pressure receiving surface 11f is opened.
On the other hand, when the oil temperature is higher than the set value, the expansion of the thermo-pellet 12a causes the valve body 12b to close, thereby closing the oil passage 11g, and the oil supply passage 8 to the second pressure receiving surface 11f. is configured to stop the introduction of hydraulic pressure.

In addition to using the valve hole 11a having a vertically elongated slit type as shown by the solid line in FIG.
As shown by the imaginary lines in FIG. 3, it may be of a continuous hole type in which a large number of small holes are vertically arranged vertically, or it may be a combination of both.

Therefore, in the above embodiment, when the engine is warmed up, when the oil temperature is lower than the set value, the temperature-sensitive control valve 12 controls the oil passage 11g as shown by the solid line in FIG.
is opened, and the oil pressure in the oil supply passage 8 reaches the oil passage 11g.
Since the pressure P1 acting on the first pressure receiving surface 11e and the pressure P2 acting on the second pressure receiving surface 11f become equal and cancel each other out, the pressure is applied to the valve body 11c of the control valve 11. Only the centrifugal force due to the rotation of the eccentric shaft 5 acts as the force in the valve opening direction.

Therefore, when the rotational speed of the eccentric shaft 5, that is, the rotational speed of the engine is low, and the centrifugal force acting on the valve body 11c is below a set value, the valve body 11c is slid downward by the spring force of the spring lld, and the circumference thereof is Since the surface closes the valve hole 11a, the oil in the oil supply passage 8 is absorbed into the hollow chamber 4 of the rotor 4.
a, and the rotor 4 is not cooled. However, when the engine speed exceeds the set value and the centrifugal force acting on the valve body 11c exceeds the set value, the valve body 11c releases the spring 11d. It moves upward against the spring force, opening the valve hole 11a, and the oil in the oil supply passage 8 is injected from the branch passage 10 toward the hollow chamber 4a and is supplied to cool the rotor 4, and further increases the engine speed. As the centrifugal force increases, the opening area of the valve hole 11a increases, and the hollow chamber 4
By increasing the amount of oil supplied to a, the rotor can be appropriately cooled in response to the increase in thermal load.

On the other hand, after the engine warms up, the oil temperature becomes higher than the set value, so the oil passage 11g is closed by the temperature-sensitive control valve 12 as shown by the phantom line in FIG.
The working oil pressure P2 on the pressure receiving surface 11f becomes zero, and the working oil pressure P1 on the first pressure receiving surface 11e and the centrifugal force due to the rotation of the eccentric shaft 5 act on the valve body 11c as forces in the valve opening direction.

Therefore, the opening timing of the control valve 11 is advanced compared to when the engine is warmed up, and even if the engine speed is low, the valve body 1
1c is a spring lld due to the above-mentioned oil pressure P1 and centrifugal force.
The valve hole 11a is opened by moving upward against the spring force, and as the centrifugal force increases due to the increase in engine speed and the oil pressure in the oil supply passage 8, that is, the working oil pressure P□ increases, the valve hole 11a opens. Since the opening area of is larger than the opening area determined only by the centrifugal force during warm-up, the amount of oil supplied from the oil supply passage 8 to the hollow chamber 4a of the rotor 4 via the branch passage 10 is increased. However, the rotor 4 is appropriately cooled in accordance with the increase in heat load accompanying the increase in engine speed.

Therefore, the rotor 4 is appropriately cooled by the oil from the oil supply passage 8, without being overcooled or insufficiently cooled, depending on the engine warm-up state and rotation speed, and the engine warm-up is maintained. At the same time, the occurrence of unburned fuel is reduced, and wear and tear on oil seal O-rings and the like is reduced.

(Effects of the invention) As explained above, according to the invention, the hydraulic pressure of the oil supply passage is applied to the valve body of the control valve, which is opened and closed by centrifugal force and is provided in the oil supply passage in the eccentric shaft. A first pressure receiving surface that presses in the valve opening direction, and a second pressure receiving surface that presses the valve body in the valve closing direction.
A temperature-sensitive control valve is provided in the oil passage forming a pressure-receiving surface and guiding the oil pressure of the oil supply passage to a second pressure-receiving surface, and when the oil temperature is below a set value, the temperature-sensing control valve controls the oil passage. By opening the oil passage and closing the oil passage using a temperature-sensitive control valve when the temperature is below the set value,
The rotor can be properly cooled at all times depending on the warm-up state and rotational speed of the engine, as well as the operating state of the engine, so warm-up of the engine can be promoted, and EC, CO, etc. It is possible to reduce the occurrence of unburned fuel, and also to reduce wear and tear on O-rings of oil seals, etc., thereby improving engine drivability and fuel efficiency.

Moreover, this invention ensures that the opening timing of the control valve is controlled only by centrifugal force without being influenced by oil pressure during warm-up when the rotor temperature is low, ensuring that the rotor is not overcooled during warm-up. It is preventable.

[Brief explanation of the drawing]

The drawings illustrate an embodiment of the present invention, and FIG. 1 is a longitudinal sectional front view showing the overall schematic configuration, FIG. 2 is an enlarged sectional view of the main part of FIG. 1, and FIG. 3 is a side view of the same. . 1...Casing, 2...Data housing, 3...Side housing, 4...
Data, 4a...Hollow chamber, 5...Eccentric shaft, 6...Rotor gear, 7...Fixed gear, 8... Oil supply passage, 9. Curved oil pump, 10... Branch passage, 11... Control valve, 11a... Valve hole, 11b... Curved case,
llc...valve body, lld...spring, lie...first pressure receiving surface, llf...second
Pressure receiving surface, l1g...Oil passage, llh...
...Drain hole, 12...Temperature-sensitive control valve, 12a.
...Thermo pellet, 12b/curve/valve body.

Claims (1)

[Scope of utility model registration request] The oil supply passage formed in the eccentric shaft includes a valve body that opens due to the centrifugal force caused by the rotation of the eccentric shaft, and a spring that biases the valve body in the valve closing direction. In a rotary piston engine that is provided with a control valve that opens and closes and controls the amount of oil supplied to the inside of the rotor, the oil pressure of the oil supply passage is applied to the valve body to push the valve body in the valve opening direction. forming a first pressure receiving surface that presses the valve body in the valve closing direction and a second pressure receiving surface that presses the valve body in the valve closing direction; When it opens,
A rotor cooling device for a rotary piston engine, comprising a temperature-sensitive control valve that closes when oil temperature exceeds a set value.