JPS62276201A - Lube feeder for rotary piston engine - Google Patents

Abstract

PURPOSE:To make it possible to operate with high speed and high duty without producing scratch, by increasing oil feeding quantity from the 2nd oil feeding port on cold start, and supplying the lube directly from the 3rd oil feeding port on the inner surface of side-housing. CONSTITUTION:In case the lube temperature detected by an oil temperature sensor 39 is under the fixed value, a control circuit 27 restricts the oil feeding quantity from the 1st oil feeding port 18 provided on the trochoid surface 2, and controls the metering oil pump 22 so as to increase the oil feeding quantity from the 2nd oil feeding port 19 provided on the inlet port 13, while the oil feeding quantity from the 1st oil feeding port 18 is restricted by the directional control value 25, and oil feeding quantity from the 3rd oil feeding port 23 provided out side of an oil seal sliding locus 12 on the inner surface of side-housing 4, and also provided inside of a corner seal sliding locus 11, is increased as much as the ristricted quantity. Thus, it is possible to prevent the scratch of side-housing 4 easily produced, when high speed or high duty is operated at cold start, more over to prevent the waste of lube.

Description

Detailed Description of the Invention 3. Detailed Description of the Invention [Field of Industrial Application] The present invention prevents scratches on the side housing that are likely to occur during high-speed, high-load operation in a cold state, and also reduces the amount of lubricating oil. This invention relates to a lubricating oil supply device for a rotary piston engine that can prevent waste as much as possible.

[Prior art]

Conventionally, in a rotary piston engine, if the engine is warmed up and operated at high speed and under high load while the engine is still warmed up, the viscosity of the lubricating oil is high, resulting in a lack of lubricating oil, and the inner surface of the side housing Scratches may occur on the real zone side, that is, on the side where the spark plug and the like are arranged and the compression/explosion stroke takes place, which causes a drop in output due to pressure escape. In order to prevent the occurrence of such scratches, for example, as shown in Japanese Unexamined Patent Publication No. 60-6001, a system is installed on the trochoid surface in order to lubricate the gas seal part separately from the main lubrication system. A first oil supply port provided at the intake port, a second oil supply port provided at the intake port, a flow rate control means for controlling the amount of lubricating oil supplied to the first oil supply port and the second oil supply port; 2. Description of the Related Art A lubricating oil supply device having a control circuit for controlling operation is known. In such conventional lubricating oil supply devices, as a flow rate control means,
For example, a metering pump is used, and lubricating oil measured in accordance with the engine load is pumped to each oil filler port and supplied to the gas seal portion of the working chamber.

Further, the ratio of the amount of lubricant supplied to the first oil filler port and the amount of lubricant oil supplied to the second filler port is usually set to be constant.

By the way, the lubricating oil supplied from the second oil supply port is sucked into the working chamber in a state mixed with intake air, so although it has good diffusivity, it is likely to be wasted due to combustion within the working chamber.

In comparison, the lubricating oil supplied from the first supply port wastes less due to combustion, and can efficiently supply lubricating oil to the trochoidal surface where the apex seal of the rotor slides.
Particularly when the viscosity of the lubricating oil is low, it is possible to sufficiently spread the lubricating oil over the entire sliding surface by supplying the lubricating oil from the first oil supply port. Therefore, from the viewpoint of increasing the oil supply efficiency in a cold state, it is advantageous to reduce the amount of lubricant supplied from the first and second oil filler ports, and increase the amount of lubricant oil supplied from the first oil filler port. However, when the viscosity of the lubricating oil is low, the lubricating oil supplied from the oil filler port tends to become like grease, which may clog the plug hole and cause a misfire. Additionally, if lubricating oil is supplied to the side housing, which is prone to scratches, by relying on the first lubricating port provided on the trochoid surface, the lubricating oil has high viscosity in cold conditions, causing the lubricating oil to reach the inner surface of the side housing. There are also problems in that it is difficult to rotate and tends to lack lubrication.

Therefore, the present applicant, for example,
As shown in the publication, separately from the main lubrication system, an oil supply port is opened in the side housing on the intake and exhaust side at or near the intersection of the trochoid minor axis and the corner seal sliding locus, and the A gas seal lubrication system for a rotary piston engine has already been proposed which is configured to pump lubricating oil. According to this invention, lubricating oil is supplied directly to the sliding contact area between the side seal attached to the side of the rotor and the side housing without intrusion of lubricating oil into the plug hole, thereby preventing scratches on the side housing. The occurrence can be effectively prevented. However, when applying such a structure to the conventional example shown in the above-mentioned Japanese Patent Application Laid-Open No. 60-6001, there is a problem that the structure of the entire lubrication system becomes complicated and expensive. .

[Purpose of the invention]

The present invention has been made in consideration of the above circumstances, and can prevent scratches on the side housing that are likely to occur during high-speed, high-load operation in a cold state by using a lubricating oil circuit that is simple in construction and inexpensive. Moreover, it is an object of the present invention to provide a lubricating oil supply device for a rotary piston engine that can prevent wastage of lubricating oil as much as possible.

[Structure of the invention]

In order to achieve the above object, the lubricating oil supply device for a rotary piston engine according to the present invention includes a first oil supply port provided on the trochoid surface, a second oil supply port provided on the intake port, and the first oil supply port provided on the intake port. In a lubricating oil supply device for a rotary piston engine, the lubricating oil supply device for a rotary piston engine includes a flow rate control means for controlling the amount of lubricating oil supplied to a filler port and a second filler port, and a control circuit that controls the operation of the flow rate control means. A third oil supply port is disposed outside the oil seal sliding trajectory and inside the corner seal sliding trajectory, and this third oil supply port supplies lubrication from the flow rate restricting means to the first oil supply port. Lubricating oil is connected to the oil supply path via a lubricating oil branch supply path, and the lubricating oil is supplied to the first oil supply port and the third oil supply port at a branch point between the lubricant oil supply path and the lubricant branch supply path or downstream thereof. A flow rate and/or directional control valve for controlling the amount of lubricant supplied is provided, and the control circuit controls the flow rate control means to limit the amount of lubricant supplied from the first oil filler port during cold operation of the engine, and While controlling the lubricant supply from the second supply port to increase, the flow rate and/or direction control valve is controlled to limit the amount of lubricant supplied to the first supply port, and the amount of lubricant supplied to the third supply port is controlled to increase the supply of lubricant from the second supply port. The control is configured to increase the supply amount.

In the rotary piston engine lubricating oil supply device configured in this way, the amount of lubricating oil supplied from the first oil supply port is limited and the lubricant supply from the second supply port is controlled to be increased. , when the engine is running cold, the second
A large amount of lubricating oil is supplied from the oil supply port, mixed with intake air, sucked into the working chamber, and widely spread and deposited on the inner surface of the side housing. In addition, the lubricant supply to the first oil filler port and the third oil filler port is restricted, and the amount of lubricant oil supplied to the first oil filler port is further restricted by the flow rate and/or the directional control valve. The supply of lubricating oil from the port is limited to the minimum amount necessary to smooth the sliding contact between the apex seal and the trochoid surface (it may be zero if a large amount of lubricant is supplied from the second oil supply port). Ru. As a result, it is possible to prevent the lubricating oil supplied from the first oil filler port from becoming grease-like and clogging the plug hole, and there is almost no possibility that the spark plug will misfire. On the other hand, the amount of lubricant supplied to the first oil supply port is restricted by the flow rate and/or direction control valve, and the amount of lubricant supplied to the third oil supply port is increased.
Lubricating oil can be sufficiently supplied from the oil filler port to the locations that require the most oil. If the third oil supply port is placed inside the oil seal sliding path, there is a risk that lubricating oil cannot be supplied to areas where scratches are likely to occur, that is, outside the oil seal sliding path on the real zone side of the side housing. Also, if the third oil supply port is arranged outside the corner seal sliding locus, the supply of lubricant is suppressed by compression pressure or explosion pressure, so there is a risk that the amount of lubricant supplied will be insufficient. In the lubricating oil supply device for a rotary piston engine of the present invention, the third oil supply port is disposed outside the oil seal sliding trajectory of the side housing and inside the corner seal sliding trajectory. It is hardly affected by the internal pressure of the working chamber, and a sufficient amount of lubricating oil can be supplied to the parts of the side housing where scratches are likely to occur.

[Embodiment 1] An embodiment of the present invention will be described below based on FIGS. 1 to 5.

A casing 1 of a rotary piston engine consists of a rotor housing 3 having a vertically elongated trochoidal inner circumferential surface (trochoidal surface) 2 and a side housing 4 that seals both end surfaces of the rotor housing 3.
A triangular rotor 6 that rotates planetarily is inserted into the rotor chamber 5 defined by . Rotor chamber 5
is divided into three working chambers 7 by the rotor 6.

The rotor 6 is supported by the side housings 4 on both sides via an eccentric shaft 8 (crankshaft), and side seals 9 are provided on both end surfaces of the rotor 6, extending in an arcuate shape along each side and slidingly contacting the side housings 4. is provided. Also, this rotor 6
Apex seals 10 are provided on each top of the rotor 6 in sliding contact with the trochoid surface 2, and corner seals 11 are provided at the joints between the side seals 9 and the apex seals 10 on both end surfaces of the rotor 6. Further, an annular oil seal 12 is provided around the eccentric shaft 8 on both end surfaces of the rotor 6 to be in sliding contact with the side housing 4.

The casing 1 is provided with an intake port 13 that passes through the side housing 4 and opens into the working chamber 7 for the intake stroke, and an exhaust port 14 that passes through the rotor housing 3 and opens into the working chamber 7 for the exhaust stroke. An intake passage 15 is connected to the port 13, and an exhaust passage 16 is connected to the exhaust port 14.

A pair of spark plugs 17 are attached to the opposite side of the rotor housing 3 from the intake port 13 and the exhaust port 14, that is, on the hot zone side.

The rotor housing 3 is provided with a first oil supply port 18 that opens into the working chamber 7 for the intake stroke, and the intake passage 15 is provided with a second oil supply port 19 that opens thereto. These first oil supply port 18 and second oil supply port 19 are connected to the first lubricating oil supply path 2o and the second lubricating oil supply path 21, respectively.
Metering oil pump 22 as a flow rate control means for controlling the amount of lubricating oil supplied to the oil filler port 18 and the second oil filler port 19
connected to. Further, on the hot zone side of the side housing 4, a corner seal 11 or an apex seal 10 is installed just before the rotor 6 finishes closing the intake port 13.
A third fuel filler port 23 is provided that opens inward from the location where the fuel filler port 23 is located. That is, when the third oil supply port 23 is opened in the zone A surrounded by the inner sliding locus 12, 12 degrees of the oil seal 12 shown in FIG. zone B1 between the inner sliding locus of the side seal 9, which requires lubricating oil, that is, the outer sliding locus 12° of the oil seal 12 and the outer sliding locus 9° of the side seal 9, and the side seal 9. The outer sliding trajectory 9° of the corner seal 11 and the outer sliding trajectory 11 of the corner seal 11
There is a risk that lubricating oil will not be supplied to zone C between Moreover, when the third oil filler port 23 is opened in the zone D outside the outer sliding trajectory tto of the corner seal 11,
The supply of lubricating oil is suppressed by the internal pressure of the working chamber 7, and there is a risk that the amount of lubricating oil will be insufficient, and the lubricating oil will be burned and wasted during the explosion stroke. Therefore, the zone B and/or
Alternatively, it is optimal to open the third oil supply port 23 in zone C. This third oil supply port 23 is connected to the metering oil pump 2
2 to the first oil supply port 18 via a lubricant branch supply path 24 . At the branch point of this lubricating oil branch supply path 24 from the first lubricating oil supply path 20, the lubricating oil supplied from the metering oil pump 22 is switched between the first oil supply port 18 side and the third oil supply port 23 side. A directional control valve 25 is provided.

In addition, a third oil supply port 2 is provided in the middle of this lubricating oil branch supply path 24.
A shutoff valve 26 that controls the timing of supply of lubricating oil from 3
is provided.

The operations of the metering oil pump 22, the directional control valve 25, and the cutoff valve 26 are controlled by a control circuit 27 composed of, for example, a microcomputer.

The metering oil pump 22 has a pair of plungers 28a and 28b, as shown in FIG. Gears 29a, 29b that mesh with a common driving worm 22a are provided on the circumferential surfaces of these plungers 28a, 28b.
are formed, and cams 30a, 3Qb are formed at one end of each of the plungers 28a, 28b. The cams 3Qa, 30b of the plungers 28a, 28b are urged by springs 32a, 32b from the other end so as to come into contact with the respective eccentric bins 31a, 31b of the eccentric shaft 31 for controlling the discharge amount. The rotation phase of this eccentric shaft 310 is transferred to the step motor 33.
By changing the positions at which the eccentric pins 31a, 31b receive the cams 30a, 30b of the plungers 28a, 28b, the plungers 28a, 2
The moving range of the plunger 8b (the strokes of the plungers 28a and 28b do not change) is changed in the axial direction thereof. Due to this change in the movement area, the plunger 28
Bumping chambers 34a, 34b formed in a, 28b
Suction ports 35a, 35b and plungers 28a, 28b
Crossover between the oil supply passage 36a opened facing the circumferential surface of the oil supply passage 36a or the discharge ports 35c, 35d from the pumping chambers 34a, 34b and the discharge passages 36b, 36c opened facing the circumferential surface of the plungers 28a, 28b. It is configured so that the discharge amount can be controlled by changing the dimensions.

The directional control valve 25 is configured to be able to switch its position between a first position where the first lubricating oil supply path 20 is communicated with the first oil filler port 18 side and a second position where the first lubricant oil supply path 20 is communicated with the third oil filler port 23 side. .

The cutoff valve 26 is configured to be opened when energized and closed when not energized.

As shown in FIG. 1, the control circuit 27 measures the amount of intake air from an air flow meter 37 provided in the intake passage 15, the engine speed and crank angle from an engine speed sensor 38, and the oil temperature from an oil temperature sensor 39. After reading the respective temperatures, the metering oil pump 22 and the directional control valve 2 are
5 and the shutoff valve 26.

That is, as shown in FIG. 4, in order to control the metering oil pump 22, the control circuit 27 reads the intake air amount from the air flow meter 37 and the engine rotation speed from the engine rotation speed sensor 38. A basic discharge amount calculation unit 40 that calculates the basic discharge amount of the ring oil pump 22 reads the engine rotation speed from the engine rotation speed sensor 38 and the oil temperature from the oil temperature sensor 39, respectively, and corrects the rotation speed correction value and oil temperature of the discharge amount. A correction amount calculation section 41a that calculates the value, and a discharge amount that calculates the discharge amount of the metering oil pump 22 by multiplying the basic discharge amount calculated by the basic discharge amount calculation section 40 by the rotation speed correction value and the oil temperature correction value. Arithmetic unit 41
b. A step number calculation section 42 that calculates the number of steps of the step motor 33 of the metering oil pump 22 corresponding to the discharge amount of the discharge amount calculation section 41b, and a calculation result of the step number calculation section 42 and the current number of steps. It has a comparison calculation unit 43 that performs a comparison calculation, and a step motor drive circuit 44 that outputs a step signal having a signal value corresponding to the calculation result of the comparison calculation unit 43 to the step motor 33.

Further, in order to control the directional control valve 25, the control circuit 27 reads the oil temperature from the oil temperature sensor 39 and determines whether the oil temperature is below a predetermined value (0° C. in this embodiment). and switches the directional control valve 25 from the first position to the second position when the oil temperature is below a predetermined value, and switches the directional control valve 25 from the second position to the first position when the oil temperature exceeds the predetermined value. A directional control valve control section 45 for switching the position is provided. Furthermore, in order to control the cutoff valve 26, the control circuit 27 reads the crank angle from the engine rotation speed sensor 38, and determines whether the crank angle is within the set angle set as the lubricant supply timing from the third oil filler port 23. The timing determination unit 46 determines whether or not the
A cutoff valve drive circuit 47 is provided that energizes the cutoff valve 26 when the crank angle is within the set angle and cuts off the energization to the cutoff valve 26 when the crank angle is outside the set angle.

The operations of the control circuit 27 that are particularly relevant to the present invention are as shown in FIG.

That is, in the above configuration, when the engine warm-up operation is started, the control circuit 27 causes the basic discharge amount calculation unit 40 to read the intake air amount from the flow meter 37 and the engine speed from the engine speed sensor 38. (31),
Calculate the basic discharge amount of the metering oil pump 22 (
S2), and the correction calculation unit 41a reads the engine speed from the engine speed sensor 38 and the oil temperature from the oil temperature sensor 39 (Sl), and calculates the basic discharge amount (S2).
Next, calculate the rotation speed correction value and oil temperature correction value for the discharge amount,
The discharge amount calculation section 41b calculates the discharge amount of the metering oil pump 22 by multiplying the basic discharge amount calculated by the basic discharge amount calculation section 40 by the rotational speed correction value and the oil temperature correction value (S3
). After this, in the step number calculation section 42, this correction calculation section 4
To calculate the number of steps of the step motor 33 of the metering oil pump 22 corresponding to the discharge amount of 1 (S4), the comparison calculation section 43 compares and calculates the calculation result of the step number calculation section 42 with the current number of steps. A step signal having a signal value corresponding to the calculation result is output from the drive circuit 44 to the step motor 33 (S5). The step motor 33 rotates in the positive or negative direction according to this step signal, moves the movement area of the plungers 28a and 28b in the axial direction, and moves the moving areas of the plungers 28a and 28b to the first lubricating oil supply path 20 and the second lubricating oil supply path 21. Adjust the lubricating oil discharge amount. Step of calculating the discharge amount of the metering oil pump 22 (S3)
If the engine temperature has not risen sufficiently and the lubricating oil temperature is below a predetermined value (0°C), the first
Since the lubricant supply amount on the lubricant oil supply path 20 side is restricted and the lubricant oil supply amount on the second lubricant oil supply path 21 side is increased, the second lubricant oil supply path 21 has no warning when the warm-up operation is completed. A larger amount of lubricating oil is supplied than later, and a larger amount of lubricating oil is mixed into the intake air from the second oil supply port 19. The lubricating oil supplied from this second oil supply port 19 is diffused into the intake air, widely spread within the working chamber 7 during the intake stroke, and adheres to the trochoid surface 2, the inner surface of the side housing 4, the circumferential surface of the rotor 6, etc. It lubricates between the trochoid surface 2 and the apex seal 10 and between the inner surface of the side housing 4 and the side seal 9 and corner seal 11. Further, when the oil temperature of the lubricating oil is below a predetermined value (0°C), the direction control valve control unit 45 that reads the oil temperature from the oil temperature sensor 39 determines that the oil temperature of the lubricating oil is the predetermined value (0°C). (S6) and switches the directional control valve 25 from the first position to the second position (S7).
Lubricating oil is supplied from the oil supply port 23. Here, lubricant oil is supplied from the third oil supply port 23 after the timing determination unit 46 confirms that the crank angle is within the set angle (S8
), the drive circuit 47 energizes the cutoff valve 26 to open it (S9), and the lubricating oil is discharged from the third oil supply port 23 (310). This third oil filler port 2
The refueling from No. 3 is repeated until the crank angle advances and deviates from the set angle. If the crank angle is outside the set angle,
The supply of lubricating oil is suppressed by the internal pressure of the working chamber 7, and in some cases, there is a risk that the fuel in the air-fuel mixture may mix into the lubricating oil in the third fuel filler port 23.
511), and as soon as the crank angle falls within the set angle, refueling from the third refueling port 23 starts. is executed (38-510).

After the warm-up operation starts, when the oil temperature exceeds a predetermined value, the viscosity of the lubricating oil is sufficiently reduced, and the lubricating oil is directly supplied from the third oil supply port 23 between the inner surface of the side housing 4 and the side seal 9 and corner seal 11. The first oil supply port 18 and the second
The space between the inner surface of the side housing 4, the side seal 9, and the corner seal 11 can be sufficiently lubricated by supplying oil from the oil supply port 19. Therefore, when it is confirmed that the oil temperature exceeds a predetermined value (S6), the directional control valve 25 is switched from the second position to the first position (S12).
The lubricating oil supply from the third oil filler port 23 is stopped, and lubricant oil is supplied from the first oil filler port 18 (313).Furthermore, when the engine temperature rises to exceed a predetermined value, the oil temperature correction value becomes 1. As a result, the restriction on the amount of lubricant supplied to the first lubricating oil supply path 20 side is lifted, and the amount of lubricant supplied to the second lubricating oil supply path 21 side is reduced.

In this way, when the oil temperature is below a predetermined value, the side housing 4
In a cold operating state where scratches are likely to occur on the side housing 4, on the one hand, the amount of lubricant supplied from the second oil filler port 19 is increased to spread the lubricating oil widely within the working chamber 7, and on the other hand, on the other hand, the lubricating oil is dispersed widely in the working chamber 7, and on the other hand, the portions of the side housing 4 where scratches are likely to occur are increased. Since lubricating oil is supplied directly from the third oil supply port 23 to the engine, it is possible to sufficiently lubricate the inner surface of the side housing 4 and the sides of the side seals 9 and corner seals 11. You can even drive without getting scratched. or,
Since the amount of refueling from the first refueling port 18 that opens on the trochoid surface 2 is limited, misfiring of the spark plug due to clogging of the plug hole due to refueling from the first refueling port 18 can be prevented, and stable warm-up operation can be achieved. can. Furthermore, the third fuel filler port 2
3 is connected to the metering oil pump 22 via the lubricating oil branch supply path 24 that branches off from the middle of the first lubricating oil supply path 20, so the entire lubrication system can be configured relatively easily and can be implemented at low cost. . In addition, since the third refueling port 23 is arranged on the hot zone side of the inner surface of the side housing 4,
The distance between the third refueling port 23, which is a refueling point, and a location that requires refueling is short, and the amount of refueling can be reduced to improve refueling efficiency.

[Embodiment 2] In the above embodiment, the third oil filler port 23 is arranged near the short axis of the trochoid surface 2, but the arrangement of the third oil filler port 23 is similar to the sliding trajectory of the oil seal 12 outside of
In addition, within the sliding trajectory of the corner seal 11, the same effect can be obtained by appropriately adjusting the timing of oil supply. For example, in another embodiment of the invention shown in FIG. 6, it is also possible to arrange the third oil filler port 23 immediately before the zone E that particularly requires lubrication. In this case, since the side seal 9 of the rotor 6 is lubricated by the lubricating oil from the third oil supply port 23 immediately before entering the scratch-prone zone E, the side seal 9 and the corner seal 11 and the side housing 4 The zone E that requires lubrication between the inner surfaces of the
The amount of lubricating oil from can be reduced to the minimum necessary limit.

Note that the arrangement of the third refueling port 23 is not limited to the hot zone side as in each of the above embodiments, but can also be arranged on the intake/exhaust side.

Further, in each of the above embodiments, the flow rate control means is constituted by the metering oil pump 22, but it is also possible to constitute the flow rate control means by, for example, a pair of variable flow rate control valves.

Furthermore, in each of the above embodiments, the flow rate and/or direction control valve that controls the amount of lubricant supplied to the first oil supply port and the third oil supply port is composed of one direction control valve 25. consists of a pair of cutoff valves arranged downstream of the branch point, a pair of variable flow control valves arranged downstream of the branch point, and a pair of variable flow control valves arranged downstream of the branch point. It is optionally possible to configure the control valve with a single control valve that is configured to control the amount of lubricating oil supplied to the first oil filler port and the third oil filler port at the same time as the direction control.

〔Effect of the invention〕

As described above, the lubricating oil supply device for a rotary piston engine of the present invention reduces the amount of oil supplied from the second oil filler port when the oil temperature is below a predetermined value and the side housing is easily scratched. The lubricating oil is spread widely within the working chamber, and on the other hand, the lubricating oil is directly supplied from the third oil supply port to the scratch-prone areas of the side housing, so that the lubricating oil is spread between the inner surface of the side housing and the side seals and corner seals. It can be sufficiently and efficiently lubricated even during cold operation, and can be operated without scratches even when operating at high speed and high load in cold operation.In addition, the opening on the trochoid surface Since the amount of refueling from the first refueling port is limited, misfiring of the spark plug due to clogging of the plug hole due to refueling from the first refueling port can be prevented, and stable warm-up operation can be achieved.

Furthermore, since the third oil supply port is connected to the flow rate control means via the lubricant branch supply path that branches off from the middle of the first lubricant supply path, the configuration of the entire lubrication system can be made relatively simple.
It can be implemented inexpensively.

[Brief explanation of the drawing]

FIG. 1 is a configuration diagram schematically showing an embodiment of the present invention, and FIG.
The figure is an explanatory diagram showing the range where the third oil filler port can be arranged, Figure 3 is a sectional view of the metering oil pump, Figure 4 is a block diagram of the control circuit, and Figure 5 is the flow of operation of this control circuit. FIG. 6 is an explanatory diagram showing the arrangement of the third fuel filler port in another embodiment of the present invention. 2 is the trochoid surface, 4 is the side housing, 11 is the corner seal, 11° is the corner seal sliding locus, 12 is the oil seal, 12° is the oil seal sliding locus, 13 is the intake port, 18 is the first oil filler port, 19 is the second fuel filler port, 2o
is the lubricating oil supply path (first lubricating oil supply path), 22 is the flow rate side f
al1 means (metering oil pump), 23 is a third oil supply port, 24 is a lubricating oil branch supply path, 25 is a flow rate and/or direction control valve (direction control valve), and 27 is a control circuit. Patent applicant Mazda Corporation Figure 1 Figure 2 Figure $5 Figure $6

Claims (1)

[Claims] 1. A first oil filler port provided on the trochoid surface, a second oil filler port provided on the intake port, and the first oil filler port and the second oil filler port provided on the intake port.
In a lubricating oil supply device for a rotary piston engine, which has a flow rate control means that controls the amount of lubricant supplied to the oil filler port, and a control circuit that controls the operation of this flow rate control means, from the oil seal sliding locus on the inner surface of the side housing. A third oil supply port is disposed on the outside of the corner seal and on the inside of the corner seal sliding locus, and this third oil supply port supplies lubrication oil in the middle of the lubricant supply path from the flow rate control means to the first oil supply port. A flow rate that is connected via an oil branch supply path and that controls the amount of lubricant supplied to the first oil supply port and the third oil supply port at a branch point between the above-mentioned lubricant supply path and the lubricant branch supply path or downstream thereof; and/or a directional control valve is provided, and the control circuit controls the flow rate control means to limit the amount of lubricant supplied from the first oil supply port and to limit the amount of lubricant supplied from the second supply port when the engine is in cold operation. While controlling the oil supply to increase, the above flow rate and/or
Or a rotary piston engine, characterized in that the directional control valve is set to limit the amount of lubricant supplied to the first oil filler port and increase the amount of lubricant oil supplied to the third filler port. Lubricating oil supply device.