JPH0652046B2 - Lubrication device for rotary piston engine - Google Patents

Abstract

PURPOSE:To achieve the stabilization of oiling and the enhancement in lubricating efficiency by providing oil filler ports on the lubricating oil supply passages, through which lubricating oil id directly supplied to an operating chamber, in such a position that the closing timing of the oil filler ports due to a rotor is immediately before the closing timing of communicating passage. CONSTITUTION:In an intermediate housing 2 positioned between two cylinders, a communicating passage 19, through which the operating chamber 8 under the compression strike in the cylinder on one side is communicated with the operating chamber 8 under intake stroke in the cylinder on the other side, is formed. In the above constitution, to the discharge ports 23, 24 of a metering oil pump 21 lubricating oil supply passages 25, 26 through which lubricating oil is directly supplied to the operating chambers 8 are connected, and the oil filler ports 25a, 26a at the respective downstream ends are opened to the operating chambers 8 through the inner circumferential surface of a rotor housing 3. And the respective oil filler ports 25a, 26a are provided in such a position that the closing timing of the oil filler ports 25a, 26a for the operating chamber 8 under compression stroke is immediately before the closing timing of the communicating passage 19.

Description

Description: TECHNICAL FIELD The present invention relates to a lubricating device for supplying lubricating oil to a working chamber in a rotary piston engine in which an intermediate housing is provided with a communication passage for reducing pumping loss. Is.

(Prior Art) Generally, in a rotary piston engine, in order to lubricate the seal portion between the inner wall surface of the casing and the rotor, lubricating oil measured by a metering oil pump is supplied to the working chamber separately from the main lubricating system. I am trying to do it. And, in order to supply the lubricating oil to the above-mentioned seal portion efficiently, in particular, a lubricating oil supply passage having an oil supply port opening to the operating chamber is provided so as to directly supply the lubricating oil from the metering oil pump to the operating chamber. Is known from the past, for example
As disclosed in Japanese Patent Application Laid-Open No. 0-3201, in addition to a passage (first lubricating oil supply passage) for supplying lubricating oil from an oil supply port opened to the intake passage through the intake passage, a passage for directly supplying lubricating oil to the working chamber ( There is known one having a second lubricating oil supply passage).

When supplying lubricating oil directly to the working chamber in this way,
In order to avoid the influence of the compression pressure, the fuel filler port is provided relatively close to the intake port, and the closing timing by the rotor of the fuel filler port for the working chamber transitioning from the intake stroke to the compression stroke is the closing timing of the intake port. It was arranged so that it would be in the vicinity. However, with such an arrangement, since the distance from the oil supply port to the position where the explosion stroke is performed is long, the lubricating oil becomes thin at the position of the explosion stroke where the largest amount of lubricating oil is required, and the lubricating efficiency is likely to decrease. On the other hand, if the oil supply port is brought close to the position of the explosion stroke, the amount of oil supply may become unstable under the influence of the compression pressure in the compression stroke. Therefore, the position of the oil supply port is an important factor for achieving good lubrication, and it has been a very difficult problem to select the proper arrangement.

Further, in a rotary piston engine, in order to reduce pumping loss due to negative intake pressure, etc., Japanese Patent Laid-Open No. 58-17
As disclosed in Japanese Patent No. 2429, in an intermediate housing between two cylinders, a communication passage that connects a working chamber in the compression stroke of one cylinder to a working chamber in the intake stroke of the other cylinder is formed. There is an intake device provided in the communication passage with a control valve for controlling the amount of ventilation of the communication passage in accordance with the negative pressure.
According to this device, when the load is low, the intake air is excessively sucked into the working chamber in the intake stroke to be reduced by the negative pressure of the intake air, and the surplus intake air is discharged to the working chamber in the intake stroke of another cylinder in the compression stroke. As a result, the pumping loss is reduced while the filling amount is adjusted according to the load.

However, in the conventional rotary piston engine equipped with such an intake device, no special consideration is given to the arrangement of the oil supply port when the lubricating oil supply passage for directly supplying the lubricating oil to the working chamber is provided, and it is effective. There was room for improvement in order to ensure proper lubrication.

(Object of the Invention) In view of such circumstances, the present invention provides a rotary piston engine having a communicating passage in an intermediate housing for reducing pumping loss, in which a lubricating oil supply passage for directly supplying lubricating oil to a working chamber is provided. In addition, the present invention provides a lubrication device for a rotary piston engine, which can improve lubrication efficiency while preventing the lubrication from the lubrication port from becoming unstable.

(Structure of the Invention) In the present invention, the intermediate housing located between the cylinders is provided with a communication passage that connects the working chamber in the compression stroke of one cylinder and the working chamber in the intake stroke of the other cylinder. In the rotary piston engine, a lubricating oil supply passage having an oil supply port opened to the working chamber is provided so as to directly supply the lubricating oil from the metering oil pump to the working chamber,
The oil supply port of the oil supply passage is provided at a position where the rotor closes the oil supply port with respect to the compression stroke working chamber immediately before the closing timing of the communication passage.

With this configuration, even during the compression stroke, the compression pressure hardly acts on the fuel filler port while the communication passage is open, and the fuel filler position is brought as close to the explosion stroke position as possible.

(Embodiment) FIGS. 1 to 3 show an embodiment of the present invention. In these drawings, reference numeral 1 denotes a casing of a two-cylinder rotary piston engine, which includes an intermediate housing 2
And two rotor housings 3 arranged on both sides of the intermediate housing 2 and having trochoidal inner peripheral surfaces, and two side housings 4 arranged outside each rotor housing 3. By these, two cylinders 5a and 5b are formed on both sides of the intermediate housing 2 with the intermediate housing 2 interposed therebetween. A substantially triangular rotor 6 is provided in each of the spaces in the cylinders 5a and 5b.
Each rotor 6 is supported by a common eccentric shaft 7, and each cylinder 5 has a phase difference of 180 °.
A planetary rotation motion is performed in the space inside a and 5b. The rotor 6 divides the space in each of the cylinders 5a and 5b into three working chambers 8, and intake, compression, explosion, expansion, and exhaust strokes are performed as the rotor 6 rotates. It is like this. The rotor 6 has an apex seal 9 on its top, side seals 10 on both sides, and corner seals 1 on both sides of the top.
1 is installed respectively.

The casing 1 is formed with an intake port that communicates with the intake passage 12 and opens into the working chamber 8 at a position where an intake stroke should be performed for each of the cylinders 5a and 5b. As shown in the figure, a primary side intake port 13 is formed in the intermediate housing 2, and a secondary side intake port 14 is formed in the side housing 4. The fuel injection valve 15 is arranged immediately upstream of the primary intake port 13. Furthermore, each cylinder 5
The rotor housings 3a, 5b are formed with exhaust ports 17 communicating with the exhaust passage 16 and opening to the working chamber 8 at a position where an exhaust stroke should be performed, and an ignition plug at a position where an explosive stroke should be performed. 18 is attached.

Further, the intermediate housing 2 is formed with a communication passage 19 that connects the working chamber 8 in one cylinder during the compression stroke and the working chamber 8 in the other cylinder during the intake stroke. Both ends of the communication passage 19 are open to the side surface of the intermediate housing 2 on the leading side of the intake ports 13 and 14, and are opened by the rotor 6 in the middle of the intake stroke and closed in the middle of the compression stroke. . This communication passage 19 allows the rotor 6 of each cylinder 5a, 5b to rotate 180
In response to the rotation with a phase difference of °, the first cylinder 5a
Of communicating the working chamber 8 during the compression stroke of the second cylinder 5b with the working chamber 8 of the second cylinder 5b during the intake stroke, and operating the working chamber 8 of the second cylinder 5b during the compression stroke during the intake stroke of the first cylinder 5a. The state of communicating with the chamber 8 is alternately generated.

A control valve 20 that opens and closes the communication passage 19 is provided in the communication passage 19, and the control valve 20 is operated by an actuator (not shown) that operates in accordance with the accelerator opening when the accelerator opening is small and the load is low. It is opened and closed under high load. In addition, when the control valve 20 is opened and the load is low, the intake passage 12 should be adjusted in order to adjust the filling amount by the communication passage 19 in a state where the regulation of intake introduction is relaxed.
The throttle valve (not shown) provided in the is adjusted to an opening larger than the opening corresponding to the required intake air amount.

Reference numeral 21 is a metering oil pump for supplying lubricating oil to the working chambers 8 of the cylinders 5a and 5b.
The lubricating oil sent from 2 to the metering oil pump 21 via an oil pump (not shown) is metered and pumped according to the engine speed and the load. The discharge ports 23 and 24 of the metering oil pump 21 have
A lubricating oil supply passage 25 for directly supplying the lubricating oil to the working chamber 8,
26 is connected, and the oil supply ports 25a and 26a at the downstream ends of the lubricating oil supply passages 25 and 26 are open to the working chamber 8 from the inner peripheral surface of the rotor housing 3. In the figure, each cylinder 5
Two lubricating oil supply passages 25 and 26, in which the oil supply ports 25a and 26a are arranged and opened in the width direction of the rotor housing 3, are provided for a and 5b, respectively.
5a and 26a are provided with refueling nozzles 25b and 26b.

Oil supply ports 25a, 26a of the lubricating oil supply passages 25, 26
Is provided at a position where the closing timing of the oil supply ports 25a, 26a by the rotor 6 with respect to the compression stroke working chamber is immediately before the closing timing of the communication passage 19, that is, immediately before the rotor 6 closes the communication passage 19. Top of the oil passes through the oil filler ports 25a and 26a,
5a and 26a are provided at positions (see FIG. 4 (B)) to be closed with respect to the working chamber 8 during the compression stroke.

Further, of the two lubricating oil supply passages 25 and 26, one lubricating oil supply passage (hereinafter, referred to as “main lubricating oil supply passage”) 25 in which the oil supply port 25a is located near the side housing 4 is provided.
Is the other lubricating oil supply passage (hereinafter referred to as "sub-lubricating oil supply passage").
It is set so that the amount of refueling is larger than that of 26). This is because the primary side intake port 13
As shown by the broken line arrow in FIG. 2, the fuel flowing into the working chamber 8 mainly passes near the oil supply port 25a of the main lubricating oil supply passage 25, and a part of the lubricating oil supplied from this oil supply port 25a This is to make up for this because it is washed away with fuel.

Further, one end of a lubricant oil return passage 27 is connected to the sub-lubricant oil supply passage 26 via a switching valve 28, and the other end of the lubricant oil return passage 27 is connected to the oil pan 22. The switching valve 28 is controlled by the control circuit 29 in response to the control valve opening / closing signal 30, so that the control valve 20 is controlled.
Is opened, the lubricating oil return passage 27 is opened to return the lubricating oil in the auxiliary lubricating oil supply passage 26 to the oil pan 22 (arrow a in FIG. 1). When the control valve 20 is closed, the lubricating oil return passage 27 is opened. 27 is closed to supply the lubricating oil from the auxiliary lubricating oil supply passage 26 to the working chamber 8 (arrow b in FIG. 1).

The communication passage 1 of the rotary piston engine as described above.
The pumping loss reducing action of 9 and the action of the lubricating device related thereto will be described with reference to FIG. In this figure, the rotor 6 of the first cylinder 5a is shown by a solid line, and the rotor 6 of the second cylinder 5b is shown by a broken line.

When the engine load is low, the control valve 20 in the communication passage 19 is opened. In this case, in the intake stroke, the intake ports 13, 14
Further, excess intake air is introduced into the working chamber 8 from the communication passage 19 to reduce the negative pressure. Then, as shown in FIG. 4 (A), from the time the rotor 6 of the first cylinder 5a closes the intake port 13 (and 14) to the time when the communication passage 19 is closed, the communication passage 19 causes the first cylinder 5a to move. Working chamber 8 during compression stroke
Is communicated with the working chamber 8 of the second cylinder 5b during the intake stroke, whereby excess intake air from the working chamber 8 of the first cylinder 5a during the compression stroke passes through the communication passage 19 and operates during the intake stroke of the second cylinder 5b. It is discharged into the chamber 8. Next, in the compression stroke after the communication passage 19 is closed as shown in FIG. 4 (B), the compression is substantially performed. Further, when the rotor 6 of each cylinder 5a, 5b rotates 180 ° from the state of FIG. 4 (A), the communication passage 19 causes the working chamber 8 of the second cylinder 5b during the compression stroke to intake the first cylinder 5a. It is connected to the working chamber 8 during the stroke, and the second
The same operation is performed for the cylinder 5b with a phase difference of 180 ° from the first cylinder 5a. In this way, the pumping loss is reduced while the filling amount according to the load is obtained.
When the load is high, the control valve 20 of the communication passage 19 is closed, so that the engine is operated in the same state as a normal engine.

By the way, the lubricating oil discharged from the metering oil pump 21 is directly supplied to the working chamber 8 through the lubricating oil supply passages 25 and 26 to lubricate the seal portion between the rotor 6 and the inner wall surface of the casing 1, and further to control valve. Also used for lubrication of 20. And, in particular, the oil supply ports 25a, 26a of the lubricating oil supply passages 25, 26 opening to the working chamber 8 are provided at positions where the closing timing thereof is immediately before the closing timing of the communication passage 19, so that the conventional ones are provided. Compared with the case where the fuel supply port is provided in the vicinity of the intake port, the fuel supply position is brought closer to the explosion stroke position that requires the most lubricating oil. In addition, when the control valve 20 of the communication passage 19 is opened, as shown in FIG. 4 (B), the rotor 6 keeps the oil supply ports 25a and 26a isolated from the working chamber 8 in the compression stroke, and then continues. Since the passage 19 is closed and the compression is substantially performed, almost no compression pressure acts on the oil supply ports 25a and 26a.

Further, in the present embodiment, the supply of oil from the auxiliary lubricating oil supply passage 26 is controlled by the switching valve 28 according to the opening / closing of the control valve 20, so that the amount of supply of oil is appropriately adjusted. That is, the discharge amount from the metering oil pump 21 can be changed according to the opening degree of the throttle valve.
When the control valve 20 is opened, the opening degree of the throttle valve is increased to some extent as described above, so that the discharge amount from the metering oil pump 21 becomes larger than the required amount according to the load. In this case, since the switching valve 28 opens the lubricating oil return passage 27, the auxiliary lubricating oil supply passage 26
The lubricating oil discharged to is returned to the oil pan 22 through the lubricating oil return passage 27, and the excessive supply of lubricating oil to the working chamber 8 is prevented.

The specific structure of the device of the present invention is not limited to the above embodiment, and various modifications can be made. For example, as the passage for supplying the lubricating oil to the working chamber 8, in addition to the lubricating oil supply passages 25 and 26 for directly supplying the lubricating oil to the working chamber 8, the lubricating oil is supplied to the working chamber 8 through the intake passage 12. Intake passage 12
It is also possible to provide a passage with an opening for the fuel filler.

Further, in the above embodiment, the control valve 20 of the communication passage 19 is switched between the open state and the closed state depending on the low load and the high load. It may be changed according to.

(Effects of the Invention) As described above, the present invention is intended to reduce the pumping loss by providing the communication passage that connects the working chamber in the compression stroke of one cylinder and the working chamber in the intake stroke of the other cylinder. In the rotary piston engine described above, since the lubricating oil supply port for supplying the lubricating oil directly to the working chamber is provided at a position where the rotor closes this lubricating port immediately before the closing timing of the communication passage, It is possible to improve the lubrication efficiency by making the refueling position as close to the explosive stroke position as possible while avoiding the influence of the compression pressure and enabling stable refueling.

[Brief description of drawings]

1 is an overall schematic view showing an embodiment of the present invention, FIG. 2 is a sectional view taken along line II-II of FIG. 1, and FIG. 3 is II of FIG.
Sectional views taken along the line I-III and FIGS. 4A to 4C are operation explanatory views. 1 ... Casing, 2 ... Intermediate housing, 5a, 5b ... Cylinder, 6 ... Rotor, 8 ... Working chamber, 19 ... Communication passage, 21 ... Metalling oil pump, 25, 26 ... Lubricating oil supply passage, 25a, 26a ...
… Filling port.

Claims (1)

[Claims] 1. A rotary piston engine in which an intermediate housing located between cylinders is provided with a communication passage for connecting a working chamber in one cylinder during a compression stroke and a working chamber in another cylinder during an intake stroke. A lubricating oil supply passage having an oil supply port opened to the working chamber so that the lubricating oil from the metering oil pump is directly supplied to the working chamber, and the lubricating oil supply port of the oil supply passage is provided by the rotor. The lubricating device for a rotary piston engine, wherein the closing timing for the compression stroke working chamber is immediately before the closing timing of the communication passage.