JP2010174740A - Lubricating device of rotary piston engine - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To suppress consumption of oil in a lubricating device of a rotary piston engine wherein oil is supplied from supply ports opened on a trochoid internal-circumferential face in a rotor housing. <P>SOLUTION: The lubricating device includes a controller 50 for controlling the mount of supply oil from the supply ports 2b, 2c in response to the state of operation of the engine 1. The controller 50 makes controls of setting the amount of the oil supply to a first specified amount when the state of operation of the engine 1 is in the state of a first operation, setting the amount of the oil supply to a second specified amount less than the first specified amount when the state of operation of the engine 1 is in the state of a second operation, and reducing the amount of supply of the oil to an amount less than the second specified amount for a specified time from the shift when the state of operation of the engine 1 is shifted from the first operation state to the second operation state. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a lubricating device for a rotary piston engine in which oil is supplied from a supply port that opens to an inner peripheral surface of a trochoid of a rotor housing.

  Conventionally, in a rotary piston engine, a lubrication system for supplying lubricating oil to a sliding surface of a gas seal separately from a lubrication system such as a bearing, as disclosed in Patent Document 1, for example, a trochoid inner periphery of a rotor housing Oil is supplied from a supply port that opens to the surface.

Moreover, in what is disclosed in the same document, the amount of oil supplied from the supply port is controlled according to the operating state of the engine. For example, the operating state of the engine is a high rotation high load state (first operating state). ), The sealability requirement between the rotor sealing member and the inner peripheral surface of the trochoid is increased. Therefore, while the oil supply amount is increased, the seal is sealed in the low rotation and low load state (second operating state). Since the demands for sex, etc. are reduced, the amount of oil supply is reduced.
JP 2008-150992 A

  However, in the lubricating device of the conventional example, when the engine operating state shifts from the first operating state to the second operating state, the oil supply amount in the first operating state is large immediately after the transition, so that the inside of the rotor housing The amount of oil in the (combustion chamber) becomes excessive, resulting in a problem of increased oil consumption.

  The present invention has been made in view of the above points, and the object of the present invention is to provide a lubricating device for a rotary piston engine that supplies oil from a supply port that opens to the inner peripheral surface of a trochoid of a rotor housing. It is to control oil consumption.

  A first aspect of the present invention is a lubricating device for a rotary piston engine in which oil is supplied from a supply port that opens to an inner peripheral surface of a trochoid of a rotor housing, and the oil from the supply port according to the operating state of the engine Control means for controlling the supply amount, wherein the control means sets the oil supply amount to a first predetermined amount when the engine operating state is the first operating state, while the engine operating state is the first operating state; In the second operation state, the oil supply amount is set to a second predetermined amount smaller than the first predetermined amount, and when the engine operation state shifts from the first operation state to the second operation state, The oil supply amount is configured to be reduced from the second predetermined amount during a predetermined period.

  Thus, when the engine operating state is the first operating state, the control means sets the oil supply amount from the supply port opened on the inner surface of the trochoid of the rotor housing to the first predetermined amount, while the engine operating state is In the second operating state, the oil supply amount is set to a second predetermined amount that is smaller than the first predetermined amount, and when the engine operating state shifts from the first operating state to the second operating state, the transition is performed for a predetermined period. By reducing the oil supply amount from the second predetermined amount, the oil supply amount is temporarily reduced immediately after the oil amount in the rotor housing becomes excessive, so that oil consumption can be suppressed. .

  According to a second aspect, in the first aspect, the first operation state is an operation state in a high rotation region, while the second operation state is an operation state in a low rotation region. Is.

  Thus, the control means sets the oil supply amount to the first predetermined amount when the engine operating state is in the high rotation region, while the oil supply amount is when the engine operation state is in the low rotation region. Is set to a second predetermined amount smaller than the first predetermined amount, and when the engine operating state shifts from the operating state in the high rotation region to the operating state in the low rotation region, 2 By reducing the amount from a predetermined amount, the oil supply amount is temporarily reduced immediately after the oil amount in the rotor housing becomes excessive, so that oil consumption can be suppressed.

  According to a third invention, in the first invention, the first operation state is an operation state in a high load region, while the second operation state is an operation state in a low load region. Is.

  Thus, the control means sets the oil supply amount to the first predetermined amount when the engine operation state is in the high load region, while the oil supply amount when the engine operation state is in the low load region. Is set to a second predetermined amount smaller than the first predetermined amount, and when the engine operating state shifts from the operating state in the high load region to the operating state in the low load region, the oil supply amount is changed for the predetermined period from the transition. 2 By reducing the amount from a predetermined amount, the oil supply amount is temporarily reduced immediately after the oil amount in the rotor housing becomes excessive, so that oil consumption can be suppressed.

  In a fourth aspect based on the second or third aspect, the control means is configured to lengthen the predetermined period as the difference between the first predetermined amount and the second predetermined amount increases. It is characterized by this.

  By the way, if the difference between the first predetermined amount and the second predetermined amount is large, the excessive amount of oil in the rotor housing immediately after the transition becomes large.

  Further, when the operating state of the engine becomes an operating state in a low rotation and low load region, a request (seal noise request) for preventing the generation of abnormal noise due to sliding of the seal member of the rotor with the inner peripheral surface of the trochoid increases.

  Here, according to the present invention, the control means makes the predetermined period longer as the difference between the first predetermined amount and the second predetermined amount increases, so that the transition increases as the excess amount of oil in the rotor housing increases. Immediately after that, the period during which the oil supply amount is temporarily reduced can be lengthened, and the oil consumption can be suppressed while satisfying the seal sound requirement.

  According to a fifth aspect of the present invention, in the second or third aspect of the present invention, the apparatus further comprises a cooling water temperature detecting means for detecting a cooling water temperature of the engine, and the control means is detected by the cooling water temperature detecting means. When the cooling water temperature is equal to or lower than a predetermined temperature, the oil supply amount is controlled according to the cooling water temperature, and the cooling water temperature detected by the cooling water temperature detecting means is less than the predetermined temperature. Is higher than the oil supply amount controlled in accordance with the operating state of the engine when the engine speed is high, it is configured to increase in the same rotational state and load state.

  By the way, when the engine coolant temperature is low, the fuel vaporization rate becomes low, and the oil in the rotor housing is washed away, and the seal member of the rotor may be worn.

  Here, according to the present invention, when the cooling water temperature of the engine detected by the cooling water temperature detecting means is not more than the predetermined temperature, the control means controls the oil supply amount according to the cooling water temperature, and the oil The supply amount is increased in the same rotational state and load state than the oil supply amount controlled according to the engine operating state when the engine coolant temperature detected by the coolant temperature detection means is higher than a predetermined temperature. Therefore, it is possible to supplement the oil that has been washed away when the engine coolant temperature is low, and to prevent wear of the seal member of the rotor.

  In a sixth aspect based on the fifth aspect, the control means is configured to decrease the increase value as the engine load is lower.

  By the way, when the operating state of the engine becomes an operating state in a low load region, the sealability requirement between the rotor sealing member and the inner peripheral surface of the trochoid is reduced.

  Here, according to the present invention, as the engine load is reduced by the control means, the increase value is reduced, so that oil consumption can be suppressed while satisfying the sealing requirement.

  According to the present invention, when the engine operating state is in the first operating state, the control means causes the oil supply amount from the supply port that opens to the inner surface of the trochoid of the rotor housing to be the first predetermined amount, while When the operating state is the second operating state, the oil supply amount is set to a second predetermined amount that is smaller than the first predetermined amount, and when the engine operating state shifts from the first operating state to the second operating state, a predetermined amount from the transition By reducing the oil supply amount from the second predetermined amount during the period, the oil supply amount is temporarily reduced immediately after the oil amount in the rotor housing becomes excessive, so that oil consumption is suppressed. be able to.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

(Entire engine configuration)
FIG. 1 shows a configuration of a main part of a rotary piston engine 1 according to an embodiment of the present invention, and FIGS. 2 and 3 show a lubricating device A arranged on a main body of the engine 1. As shown in FIG. 1, a rotor housing chamber 4 surrounded by a bowl-shaped rotor housing 2 having a trochoid inner peripheral surface 2a and side housings 3, 3,... A rotor 6 having a shape is accommodated, and three working chambers 5, 5, and 5 are formed on the outer peripheral side thereof. As shown in FIG. 3, the engine 1 according to this embodiment includes two rotor housings 2, 2 sandwiched between three side housings 3, 3.

  A front cover 7 is disposed on the front side of the engine shown on the right side in FIG. 3, and the front end of an eccentric shaft 8 (hereinafter also simply referred to as the shaft 8) that protrudes through substantially the center of the front cover 7 is used for driving auxiliary equipment. While pulleys 9 and 10 are disposed, a flywheel 11 is disposed at the rear end of the shaft 8. Hereinafter, in this specification, among the three side housings 3, 3, 3 arranged in the front-rear direction of the engine 1, the central one is referred to as an intermediate housing 3 when distinguished from the front and rear sides.

  As shown in FIG. 1, the rotor 6 is rotatably supported with respect to the eccentric wheel 8 a of the eccentric shaft 8 that penetrates the side housing 3, and although not shown in the drawing, the rotor 6 is formed inside the rotor 6. The gear meshes with a fixed gear (external gear) on the side housing 3 side, and thereby performs planetary rotational movement with a defined movement trajectory. That is, the rotor 6 rotates around the eccentric ring 8a of the shaft 8 while the three outer peripheral top portions (apex seals 16, 16,...) Are in sliding contact with the trochoid inner peripheral surface 2a. Revolves around the axis X.

  During the movement of the rotor 6, the working chambers 5, 5,... Formed between the tops of the rotor 6 move in the circumferential direction (clockwise in the figure), respectively. Thus, four strokes of intake, compression, expansion (combustion) and exhaust are performed, and the pressure due to the combustion rotates the shaft 8 via the rotor 6. For example, in FIG. 1, the working chamber 5 (upper working chamber in the drawing) communicating with the intake port 12 is at the bottom dead center of the intake and shifts to the compression stroke as the rotor 6 rotates.

  Thus, the air-fuel mixture is compressed inside the working chamber 5 which has shifted to the compression stroke, and is ignited by the spark plugs 13 and 14 at a predetermined timing from the final stage of the compression stroke to the expansion stroke, and the combustion / expansion stroke is performed. The working chamber 5 located in the lower right in FIG. 1 is in the first half of the combustion / expansion stroke. When the rotor 6 moves and the working chamber 5 communicates with the exhaust port 15, the working chamber 5 shifts to the exhaust stroke. The working chamber 5 located in the lower left of the figure is in the final stage of the exhaust stroke. Such a combustion cycle is performed once for every three rotations of the shaft 8 for each working chamber 5. Since there are three working chambers 5 for each rotor 6, combustion is performed once for each rotation of the engine 1. It will be.

  In order to prevent the high-pressure gas due to such combustion from blowing through the working chamber 5, apex seals 16 are respectively provided in the three top portions of the outer periphery of the rotor 6 in the rotor width direction (direction perpendicular to the paper surface of FIG. 1). , 16,... Are arranged. In addition, arcuate side seals 17, 17,... Are arranged on both side surfaces of the rotor 6 so as to connect the adjacent top portions, and an opening is formed on one side at a portion where both the seal members are joined. A generally cylindrical corner seal 18, 18,. Each of the seal members 16 to 18 is fitted in a groove formed in the rotor 6 and is urged outward by a spring member (not shown).

  The engine 1 of this embodiment is of a side intake / side exhaust type in which both intake and exhaust ports open to the side surfaces of the side housings 3, 3,. That is, the intermediate housing 3 is formed with a pair of first intake ports 12 and 12 that are arranged in the longitudinal direction of the engine and open toward the rotor accommodating chambers 4 and 4, respectively. On the other hand, the side housings 3 and 3 are formed with second and third intake ports 20 and 21, respectively, as shown only in FIG.

  Similarly, in the intermediate housing 3, a pair of first exhaust ports 15 and 15 are formed below the first intake ports 12 and 12 in the longitudinal direction of the engine and face the rotor accommodating chambers 4 and 4, respectively. On the other hand, second exhaust ports 22 and 22 are formed in the side housings 3 and 3 below the second and third intake ports 20 and 21, respectively.

  The first to third intake ports 12, 20, and 21 are connected to intake ports 12, 20, and 21 through intake manifolds (not shown) according to the operating state of the engine 1. A variable intake system to be switched is connected. A throttle valve that restricts the flow of intake air and adjusts its flow rate is arranged upstream of the intake system, and fuel is injected into each branch passage that branches to the ports 12, 20, and 21 on the downstream side. An injector is disposed.

  Further, an air flow sensor 23 (schematically shown in FIG. 2) for measuring an intake air flow rate Q adjusted by a throttle valve is disposed upstream of the intake system. Further, as shown in FIG. 3, an electromagnetic rotation angle sensor (an eccentric angle sensor 24) that detects the rotation angle is disposed on the front end side of the eccentric shaft 8. Furthermore, a cooling water circuit (not shown) of the engine 1 is provided with a cooling water temperature sensor 25 (schematically shown in FIG. 2) for detecting the cooling water temperature of the engine 1. ing.

(Lubrication system configuration)
In the engine 1 of this embodiment, a dedicated lubricating device A for supplying oil for lubrication (engine oil) directly to the gas seal portion by the apex seals 16, 16,... And the side seals 17, 17,. ing. The lubrication apparatus A takes out oil from an oil gallery for supplying oil to the main bearing of the shaft 8, adjusts the pressure by an oil control valve 30 (OCV), and then performs metering (measuring) and oil pumps 31, 32. , And is sent out to the nozzles 40,..., 41,... Facing the inner surface 2a of the trochoid of the rotor housing 2.

  The OCV 30 and the oil pumps 31, 32 are controlled via a driver circuit 51 by a controller 50 (Programmable Control Module: hereinafter abbreviated as PCM) as schematically shown in FIG. As will be described in detail later, the PCM 50 is a control unit that controls the oil pumps 31 and 32 based on at least signals from the air flow sensor 23, the exhaust angle sensor 24, and the coolant temperature sensor 25. Based on a signal from an oil pressure sensor 52 attached to the oil pump 32, feedback control is performed, and a timer counter or the like (not shown) is provided.

  Then, the oil whose pressure is adjusted by the control of the OCV 30 is sent to the first oil pump 31 through the upstream pipe 33, and is distributed to the nozzles 40,. The oil is sent to the second oil pump 32 on the downstream side through the intermediate pipe 34. The oil is distributed to the nozzles 41, 41 by the operation of the second oil pump 32, and surplus oil is sent to the oil filler pipe (not shown) by the downstream pipe 35 to the oil gallery of the engine 1. Is returned.

  As shown in FIGS. 1 and 3, the first and second oil pumps 31 and 32 are arranged side by side in the moving direction of the rotor 6 above the engine 1 (above the intermediate housing 3 in the illustrated example). , 37 (omitted in FIG. 2), are attached to the upper parts of the housings 2, 3,. The first oil pump 31 on the upstream side is positioned lower than the second oil pump 32 on the downstream side, and is positioned on the advance side in the moving direction of the rotor 6.

  In the first oil pump 31, the oil suction port P to which the upstream side pipe 33 is connected is located at a lower position (downward) than the oil return port R to which the upstream end of the intermediate pipe 34 is connected. On the other hand, the oil suction port P to which the downstream end of the intermediate pipe 34 is connected in the downstream second oil pump 32 is located higher than the oil return port R of the first oil pump 31 and the downstream pipe. It is in a position lower than the oil return port R to which 35 is connected.

  In other words, the oil always flows upward in the supply path that starts from the OCV 30 and connects the two oil pumps 31 and 32 in series, so that air is mixed into the oil sucked into the first oil pump. Even so, it naturally goes from the intermediate pipe 34 to the second oil pump 32. In the second oil pump 32 as well, the air mixed into the oil naturally goes to the downstream pipe 35.

  Further, the first and second oil pumps 31 and 32 are provided with a plurality of oil discharge ports D to which oil supply pipes 38 to the nozzles 40 to 41 are connected, respectively. These oil discharge ports D,... Are positioned lower than the oil suction port P and the return port R in the oil pumps 31 and 32 (the oil at a relatively higher position of the first oil pump 31). The discharge ports D and D are almost the same height as the oil suction port P, but the oil discharge ports D and D are slightly lower.

  Thus, in each of the two oil pumps 31, 32, the oil discharge ports D,... Are at a relatively low position (that is, relatively downward), so that air is mixed into the oil sucked from the oil suction port P. However, it is difficult for the air to go to the oil discharge ports D,... Located below, but to the oil return port R located above. That is, oil discharged from the oil discharge ports D,... At relatively low positions in the oil pumps 31, 32, and sent to the nozzles 40, ..., 41, ... by the oil supply pipes 38, ..., 39, ... It is difficult for air to enter.

  Here, the oil supply pipes 38,... Connected to the oil discharge ports D,... Of the first oil pump 31 are arranged at the downstream ends of the rotor housing 2 near both sides in the rotor width direction (engine longitudinal direction). It is connected to the side nozzles 40. On the other hand, the downstream ends of the oil supply pipes 39,... Connected to the oil discharge ports D,... Of the second oil pump 32 are connected to center nozzles 41, 41 disposed substantially at the center in the rotor width direction.

  As shown in an enlarged view in FIG. 4, the center nozzles 41, 41 are arranged one by one for each rotor housing 2, and have a substantially central portion in the rotor width direction from the outer periphery of the rotor housing 2 to the trochoid inner peripheral surface 2 a. It is inserted into the fitting hole 2b (center supply port) that penetrates. The ends of the oil supply pipes 38 are connected to the upper end of the center nozzle 41 and fastened with bolts. The oil supplied from the center nozzles 41, 41 to the approximate center of the inner surface 2a of the trochoid is used for lubrication with the apex seals 16,.

  On the other hand, two side nozzles 40 are arranged for each rotor housing 2, and are formed at a predetermined distance apart on the advancing side in the moving direction of the rotor 6 on both sides of the insertion hole 2b of the center nozzle 41. The pair of insertion holes 2c and 2c (side supply ports) are inserted. The pair of fitting insertion holes 2c, 2c are formed in a square shape that is separated from each other toward the lower end side. The oil supplied from the side nozzles 40, 40 to both sides of the trochoid inner peripheral surface 2a wraps around the side surface of the side housing 3, and between the side seals 17,... And the corner seals 18,. Used for lubrication.

  That is, in the lubricating device A of this embodiment, two side nozzles 40 and 40 and one center nozzle 41 are disposed for each of the two rotor accommodating chambers 4 and 4, for a total of six nozzles 40,. 41, ... are used. Of these, four side nozzles 40,... Are supplied with oil from the first oil pump 31 through four oil supply pipes 38,..., And the two center nozzles 41, 41 are supplied with two oil supply pipes 39,. The oil is supplied from the second oil pump 32 by 39 respectively.

  As described above, the first oil pump 31 is located on the more advanced side than the second oil pump 32 in the moving direction of the rotor 6 above the engine 1, and oil is sent from the first oil pump 31. The side nozzles 40 are positioned on the advance side in the moving direction of the rotor 6 relative to the center nozzle 41 on the inner surface 2a of the trochoid. This makes it easy to align the oil flow distance from the first oil pump 31 to the side nozzles 40,... With the distance from the second oil pump 32 to the center nozzles 41, 41. It is advantageous to improve controllability by aligning control responsiveness of the amount of oil supplied from the nozzles 40,.

  By the way, in this embodiment, basically the same metering oil pump is used as the first and second oil pumps 31 and 32. This originally has four oil discharge ports. As shown in detail in FIG. 5, the first oil pump 31 is shown in detail, and the rod 43c is made to have its axis (axis Z) by an electromagnet 43b covered with a cover 43a. ), And an electromagnetic actuator 43 (driving mechanism unit) that is driven back and forth in the direction, and a pump body 44 including a plunger 44a that is driven thereby.

  Although only two are shown in the figure, the pump body 44 is formed with four plunger chambers 44b,... For accommodating the four plungers 44a,..., Respectively, and communicates with the main passage 44c on the suction side. In addition, the base end side (upper side in the drawing) of each plunger chamber 44 b,... Communicates with a disc storage chamber 44 d formed on the base end side of the pump body 44. The disc storage chamber 44d is circular in cross section, and is communicated with the main passage 44c not only by the plunger chambers 44b, but also by a passage 44e that bypasses them.

  The tip of a rod 43c protrudes from the electromagnetic actuator 43 side at the center of the disk accommodating chamber 44d, and a disk-shaped disk 43d is fixed thereto. This disk 43d connects the rod 43c of the electromagnetic actuator 43 and the four plungers 44a,... When the disk 43d moves in the disk storage chamber 44d in the axis Z direction by the advancement / retraction of the rod 43c, the disk 43d is integrated therewith. The four plungers 44a, ... are driven forward and backward.

  That is, when the disk 43d moves to one side (upper side in the figure) in the axis Z direction by the retraction of the rod 43c, the four plungers 44a,... Also retreat, and the plunger chambers 44b,. A predetermined amount of oil is inhaled. When the disc 43d moves to the other side in the axis Z direction (lower side in the figure) by the advancement of the rod 43c, the four plungers 44a,... Also move forward, whereby oil is discharged from the tips of the plunger chambers 44b,. It is pushed out into the communication passage 44f to the outlets D,.

  In the example shown in the figure, the communication passages 44f,... Extend straight from the tips of the plunger chambers 44b,... And contain a check valve 44g that prevents backflow of oil, and a portion that opens at the end face of the pump body 44 is plugged. It is sealed, and oil discharge ports D,. Bolts 44h for fastening the ends of the oil supply pipes 38, ... are screwed into the oil discharge ports D, ..., and oil flows through the passages in the bolts 44h and is discharged to the oil supply pipes 38, .... Is done.

  In addition, the code | symbol 44i of illustration shows the cylindrical connector screwed in to the oil inlet P, and the downstream end of the upstream piping 33 is fitted by this connector 44i. Further, as indicated by phantom lines in the figure, the pump body 44 is also formed with an oil return flow path 44j extending from the disk storage chamber 44d to the oil return port R.

  The oil pump having the above-described configuration is usually arranged so that the driving direction (axis Z) of the plungers 44a,... By the electromagnetic actuator 43 is substantially horizontal, and the oil is transmitted from the disk housing chamber 44d to the outer periphery of the rod 43c. By reaching inside the electromagnetic actuator 43, it is used for lubrication of the rod 43c and cooling of the electromagnet 43b.

  However, in this embodiment, as described above, in the first and second oil pumps 31, 32, the pump body 44 is placed more than the electromagnetic actuator 43 so that the discharge ports D,. In this case, for example, as shown in FIG. 5, it is conceivable that the axis Z is directed in the vertical direction (vertical direction), but the oil pump 31, 32 is inclined (see FIGS. 1 and 2).

  This is because, in the supply path in which the two oil pumps 31 and 32 are interposed in series as described above, the oil always flows upward in the oil pumps 31 and 32 than the oil return port R. This is because the suction port P is positioned low, and the oil can be distributed to the electromagnetic actuator 43 by tilting the oil pumps 31 and 32 in this manner. For this purpose, the axis Z is inclined by about 45 ° with respect to the vertical direction, but for example, it may be inclined by about 30-60 °.

  Then, in the pump body 44 of the oil pumps 31 and 32 that are appropriately tilted, oil flows from the main passage 44c on the suction side to the disc storage chamber 44d through the plunger chamber 44b,... And the bypass passage 44e. As described above, the required amount of oil is discharged by the forward / backward movement of the plungers 44a,..., While the excess oil is discharged from the disk storage chamber 44d through the return passage 44j and from the oil return port R. At this time, the air mixed in the oil naturally comes to the upper oil return port R, and is separated from the oil discharged from the lower discharge ports D,.

  Furthermore, in this embodiment, the mixed air is separated from the oil discharged from the individual oil pumps 31 and 32. In this embodiment, the second oil pump 32, which is located at a relatively high position, is originally used. Of the four outlets D,..., Only two of the lower positions are used, and the oil supply pipes 39 and 39 are connected to each of the four outlets D,. That is, out of the eight original oil discharge ports D,... That is the combination of the two oil pumps 31, 32, air is relatively easily mixed into the oil discharged at the highest discharge port. By not doing so, the oil-mixed air is more reliably separated.

(Oil supply control)
Next, oil supply control in the lubricating device A configured as described above will be described. In this embodiment, the rotary piston engine 1 to which the lubricating device A is applied is of a side exhaust type in which the exhaust ports 15 and 22 are opened on the side surfaces of the side housings 3, 3,. During high revolutions with a large exhaust flow rate, the thermal load on the side of the rotor 6 increases and the lubrication requirement increases, while on the low load side and low revolution side, the lubrication requirement on the side of the rotor 6 decreases.

  More specifically, FIG. 6 shows the lubrication requirements for each operation region of the engine 1. First, in the region of low load and low rotation, the generation of noise due to the sliding of the apex seal 16 with the inner surface 2a of the trochoid is prevented. If there is a request (seal noise request) and the load is high even at low rotation, it is necessary to wash out the carbon adhering to each seal member 16 to 18 with combustion to prevent sticking (reliability requirement ( Seal stick)).

  Further, in the middle load middle rotation region where the actual use frequency is high, the sealability requirement with the sliding portion, which is the original function of each seal member 16-18, becomes dominant. This requirement for sealing performance becomes higher in a high load region where the combustion pressure increases. In order to obtain a high output, it is necessary to increase the oil supply amount (output performance requirement). Further, in the high-load high-rotation region, an increase in the amount of oil supply is required in order to prevent wear of the seal members 16 to 18 and their sliding surfaces (requirement of reliability (gas seal etc.)).

  As such, the lubrication requirements that differ depending on the operating state of the engine 1 are arranged by item, and which lubrication requirement of the outer periphery and the side portion of the rotor 6 is strong for each requirement item (which oil on the trochoidal surface and the side surface) Table 1 below shows whether the supply amount must be increased).

  In Table 1, among the outer periphery (trochoid inner peripheral surface) and the side portion (side surface) of the rotor 6, the one with the greater lubrication requirement is marked with a circle. That is, it is sufficient to prevent the generation of the sliding sound of the apex seal 16 in response to the request for the sealing noise in the low load and low rotation region, and it is sufficient to supply oil to the inner surface of the trochoid. Similarly, it is necessary to supply oil to the inner peripheral surface of the trochoid for the carbon stick (requirement of reliability) of the apex seal 16 at the time of high load and low rotation.

  In addition, since the gas sealability related to all of output, torque, and emission (EM) is an original function of each of the seal members 16 to 18, the trochoid surface and the side surface of the entire operation region can meet this requirement. Although it is necessary to supply oil to both, since the lubrication requirement of the apex seal 16 is relatively strong, the amount of oil supplied to the trochoid surface is larger. In order to suppress wear of the apex seal 16 at high load and high rotation, it is necessary to increase the amount of oil supplied to the trochoid surface.

  Further, as a reliability requirement at the time of high load and low rotation, the carbon sticks of the side seal 17 and the corner seal 18 must be prevented. From this point, it is necessary to increase the amount of oil supplied to the side surface. . Similarly, wear of the side seal 17 and the corner seal 18 as well as the apex seal 16 must be suppressed at the time of the high load and high rotation. From this point, it is necessary to increase the amount of oil supplied to the side surface.

  In short, in the low load and low rotation region of the engine 1, oil only needs to be supplied to the inner surface of the trochoid, that is, the outer periphery of the rotor 6, but to the side of the rotor 6 in response to an increase in engine load or rotational speed. However, there is a need to supply oil, and the higher the load or rotation speed, the greater the amount of oil supplied to both.

  Therefore, in the lubrication apparatus A of this embodiment, the operation of the two oil pumps 31 and 32 provided on the upper portion of the engine 1 as described above is controlled by the PCM 50 according to the operating state of the engine 1, respectively. The amount of oil supplied from the center and side nozzles 40,..., 41,.

  That is, the PCM 50 first calculates the intake charge efficiency into each working chamber 5 based on the signals from the air flow sensor 23 and the eccentric angle sensor 24, and regards this as the load state of the engine 1. Then, based on the engine load and the engine rotational speed obtained from the signal from the eccentric angle sensor 24 (that is, based on the operating state of the engine 1), referring to the normal control map as shown in FIG. , 41,..., That is, oil discharge amounts from the first and second oil pumps 31, 32 are calculated.

  The normal control map shown in FIG. 7 is obtained by investigating and setting appropriate oil supply amounts from the nozzles 40,..., 41,. When the operating range of the engine 1 is equally divided into three rotation ranges of low, medium, and high according to the rotational speed, most of the low rotation range (except for some areas on the relatively high load high rotation side) and the middle The oil is supplied only by the center nozzles 41,... In some areas on the low load side in the rotation region, while the oil is supplied by both the center and side nozzles 40,. It is to be supplied.

  In the normal control map, for example, the change in oil supply amount (flow rate) when the engine speed increases in the full load (WOT) state, and the oil when the engine load increases while the engine speed remains constant at ne1 The change in supply amount (flow rate) is shown in the figure, and the oil supply amount by the center and side nozzles 40,..., 41,. At the same time, the ratio of the oil supply amount from the side nozzles 40,... To the oil supply amount from the center nozzles 41,.

  The PCM 50 operates the first and second oil pumps 31 and 32 based on the target value of the oil supply amount to each of the nozzles 40,..., 41,. To control. As described above, the oil is discharged from the oil pumps 31 and 32 by the advance / retreat operation of the plungers 44a,..., And the stroke volume is constant, so the discharge amount is the advance / retreat operation of the plungers 44a,. It is controlled by the frequency (number of operations per predetermined time).

  Therefore, according to the lubrication apparatus A according to this embodiment, the PCM 50 performs the operation based on the operating state of the engine 1 detected based on the signals from the air flow sensor 23 and the eccentric angle sensor 24 during the operation of the rotary piston engine 1. The first and second oil pumps 31 and 32 are respectively controlled, and oil is supplied to the trochoid inner peripheral surface 2a of the rotor housing 2 from the center and side nozzles 40,..., 41,. Will come to be.

  That is, when the engine 1 is on the relatively low load and low rotation side, oil is supplied only by the center nozzles 41,..., And the outer periphery (apex seal 16) of the rotor 6 is mainly lubricated, and the apex seal 16 and the trochoid Generation of abnormal noise due to sliding with the inner peripheral surface 2a is prevented. At this time, since the lubrication requirement on the side of the rotor 6 is low, sufficient lubrication is performed by the oil leaking from the bearing of the shaft 8, and the oil does not have to be supplied from the side nozzles 40,. Therefore, consumption of engine oil is suppressed.

  On the other hand, as the engine load or the rotational speed increases, the temperature rise at the side of the rotor 6 due to exhaust increases, and if the lubrication requirement becomes stronger, not only the center nozzle 41, but also the side nozzles 40,. Will be supplied. As a result, the oil is sufficiently supplied to each of the seal members 16 to 18, and the original gas seal function is exhibited. In particular, at low rotation and high load, the oil flushes the carbon from the seal members 16 to 18 and prevents the stick.

  As the engine load or rotational speed increases, the amount of oil supplied to the outer periphery and the side of the rotor 6 increases, and even if the combustion pressure increases for a high load, the gas blow-off from the working chamber 5 is prevented. High output can be obtained. Further, in the high-load and high-rotation range, wear of the seal members 16 to 18 and their sliding surfaces can be prevented by increasing the oil supply amount.

  That is, according to the lubrication apparatus A of this embodiment, the amount of oil supplied to the vicinity of the central portion of the trochoid inner peripheral surface 2a in the width direction of the rotor 6 and to the side thereof is respectively determined on the outer periphery and the side portion of the rotor 2. Therefore, the consumption of engine oil can be suppressed while satisfying the lubrication requirements of each part.

  In the lubrication apparatus A of this embodiment, as described above, the PCM 50 is configured such that the operating state of the engine 1 is in a certain operating state in the high speed region (hereinafter referred to as a first high speed operating state. In the operation state), the oil supply amount from the side nozzles 40 is set to a predetermined supply amount (hereinafter referred to as a first supply amount. The first predetermined amount in the present invention), while the operation state of the engine 1 is set. Is a certain operation state in the low rotation region (hereinafter referred to as a first low rotation operation state. The second operation state in the present invention), the oil supply amount from the side nozzles 40,. The predetermined supply amount (hereinafter referred to as the second supply amount, referred to as the second predetermined amount in the present invention) is set to be smaller (see FIG. 7).

  By the way, when the operation state of the engine 1 shifts from the operation state in the high rotation region to the operation state in the low rotation region, immediately after the transition, the oil supply amount in the operation state in the high rotation region is large. The problem is that the amount of oil in the chamber 4) (combustion chamber) becomes excessive and oil consumption increases.

  Therefore, in this embodiment, when the operation state of the engine 1 shifts from the first high rotation operation state to the first low rotation operation state, the PCM 50 starts from the side nozzles 40,. The oil supply amount is reduced from the second supply amount. As a result, immediately after the transition in which the amount of oil in the rotor housing 2 becomes excessive, the amount of oil supplied from the side nozzles 40 can be temporarily reduced, and oil consumption can be suppressed.

  By the way, if the difference between the first supply amount and the second supply amount is large, the excess amount of oil in the rotor housing 2 immediately after the transition becomes large. Further, as described above, when the operation state of the engine 1 becomes an operation state in the low rotation and low load region, the seal sound request becomes high.

  Therefore, in this embodiment, the PCM 50 increases the predetermined period as the difference between the first supply amount and the second supply amount increases. As a result, as the excess amount of oil in the rotor housing 2 increases, the period for temporarily reducing the oil supply amount immediately after the transition can be lengthened, and the oil consumption can be suppressed while satisfying the seal sound requirement. Can do.

  By the way, when the cooling water temperature of the engine 1 is low, the vaporization rate of the fuel is lowered, the oil in the rotor housing 2 is washed away, and the seal members 16 to 18 of the rotor 6 may be worn.

  Therefore, in this embodiment, when the cooling water temperature of the engine 1 detected by the cooling water temperature sensor 25 is equal to or lower than the predetermined temperature, the PCM 50 sets the oil supply amount from the side nozzles 40,... According to the cooling water temperature. The oil supply amount is controlled more than the oil supply amount controlled according to the operating state of the engine 1 when the coolant temperature of the engine 1 detected by the coolant temperature sensor 25 is higher than the predetermined temperature. In the same engine rotation state and load state, the amount is increased. Thereby, it is possible to supplement the oil that has been washed away when the cooling water temperature of the engine 1 is low, and to prevent the seal members 16 to 18 of the rotor 6 from being worn.

  By the way, as described above, when the operating state of the engine 1 becomes an operating state in the low load region, the sealing requirement is reduced.

  Therefore, in this embodiment, the PCM 50 decreases the increase value as the load on the engine 1 is lower. Thereby, oil consumption can be suppressed, satisfy | filling sealing performance request | requirement.

  In the lubricating device A of this embodiment, as described above, the PCM 50 is configured so that the operation state of the engine 1 is a certain operation state in the high rotation region (hereinafter referred to as a second high rotation operation state. In the present invention). In the first operation state), the amount of oil supplied from the center nozzles 41,... Is set to a predetermined supply amount (hereinafter referred to as a third supply amount. The first predetermined amount in the present invention), while the engine 1 When the operation state is a certain operation state in the low rotation region (hereinafter referred to as a second low rotation operation state, the second operation state in the present invention), the amount of oil supplied from the center nozzles 41,. The predetermined supply amount is smaller than the supply amount (hereinafter referred to as the fourth supply amount; the second predetermined amount referred to in the present invention) (see FIG. 7).

  In the lubricating device A of this embodiment, the amount of oil supplied from the center nozzles 41,... Is controlled as follows for the same reason as described above.

  That is, when the operation state of the engine 1 shifts from the second high rotation operation state to the second low rotation operation state, the PCM 50 reduces the oil supply amount from the center nozzles 41,. The amount is reduced from the fourth supply amount. As a result, immediately after the transition in which the amount of oil in the rotor housing 2 becomes excessive, the amount of oil supplied from the center nozzles 41 can be temporarily reduced, and oil consumption can be suppressed.

  Further, the PCM 50 increases the predetermined period as the difference between the third supply amount and the fourth supply amount increases. As a result, as the excess amount of oil in the rotor housing 2 increases, the period for temporarily reducing the oil supply amount immediately after the transition can be lengthened, and the oil consumption can be suppressed while satisfying the seal sound requirement. Can do.

  Further, when the cooling water temperature of the engine 1 detected by the cooling water temperature sensor 25 is equal to or lower than a predetermined temperature, the PCM 50 controls the amount of oil supplied from the center nozzles 41,. The oil supply amount is the same engine rotation state as the oil supply amount controlled according to the operating state of the engine 1 when the coolant temperature of the engine 1 detected by the coolant temperature sensor 25 is higher than the predetermined temperature. In the load state, the amount is increased. Thereby, it is possible to supplement the oil that has been washed away when the cooling water temperature of the engine 1 is low, and to prevent the seal members 16 to 18 of the rotor 6 from being worn.

  Furthermore, the PCM 50 is configured to decrease the increase value as the load of the engine 1 is lower. Thereby, oil consumption can be suppressed, satisfy | filling sealing performance request | requirement.

  On the other hand, in the lubrication apparatus A of this embodiment, as described above, the PCM 50 is configured such that the operation state of the engine 1 is a certain operation state in the high load region (hereinafter, referred to as a first high load operation state. In the first operation state), the oil supply amount from the side nozzles 40,... Is set to a predetermined supply amount (hereinafter referred to as a fifth supply amount. The first predetermined amount in the present invention), while the engine 1 When the operation state is a certain operation state in the low load region (hereinafter referred to as a first low load operation state. The second operation state in the present invention), the oil supply amount from the side nozzles 40,. A predetermined supply amount that is smaller than the supply amount (hereinafter referred to as a sixth supply amount; a second predetermined amount in the present invention) is set (see FIG. 7).

  By the way, when the operation state of the engine 1 shifts from the operation state in the high load region to the operation state in the low load region, the oil supply amount in the operation state in the high load region is large immediately after the transition. The amount becomes excessive, causing the problem of increased oil consumption.

  Therefore, in this embodiment, when the operation state of the engine 1 shifts from the first high load operation state to the first low load operation state, the PCM 50 starts from the side nozzles 40,. The oil supply amount is reduced from the sixth supply amount. As a result, immediately after the transition in which the amount of oil in the rotor housing 2 becomes excessive, the amount of oil supplied from the side nozzles 40 can be temporarily reduced, and oil consumption can be suppressed.

  By the way, if the difference between the fifth supply amount and the sixth supply amount is large, the excessive amount of oil in the rotor housing 2 immediately after the transition becomes large. Further, as described above, when the operation state of the engine 1 becomes an operation state in the low rotation and low load region, the seal sound request becomes high.

  Therefore, in this embodiment, the PCM 50 increases the predetermined period as the difference between the fifth supply amount and the sixth supply amount increases. As a result, as the excess amount of oil in the rotor housing 2 increases, the period for temporarily reducing the oil supply amount immediately after the transition can be lengthened, and the oil consumption can be suppressed while satisfying the seal sound requirement. Can do.

  By the way, as described above, when the cooling water temperature of the engine 1 is low, the fuel evaporation rate is low, the oil in the rotor housing 2 is washed away, and the seal members 16 to 18 of the rotor 6 may be worn. is there.

  Therefore, in this embodiment, when the cooling water temperature of the engine 1 detected by the cooling water temperature sensor 25 is equal to or lower than the predetermined temperature, the PCM 50 sets the oil supply amount from the side nozzles 40,... According to the cooling water temperature. The oil supply amount is controlled more than the oil supply amount controlled according to the operating state of the engine 1 when the coolant temperature of the engine 1 detected by the coolant temperature sensor 25 is higher than the predetermined temperature. In the same engine rotation state and load state, the amount is increased. Thereby, it is possible to supplement the oil that has been washed away when the cooling water temperature of the engine 1 is low, and to prevent the seal members 16 to 18 of the rotor 6 from being worn.

  By the way, as described above, when the operating state of the engine 1 becomes an operating state in the low load region, the sealing requirement is reduced.

  Therefore, in this embodiment, the PCM 50 decreases the increase value as the load on the engine 1 is lower. Thereby, oil consumption can be suppressed, satisfy | filling sealing performance request | requirement.

  In the lubricating device A of this embodiment, as described above, the PCM 50 is configured such that the operating state of the engine 1 is a certain operating state in the high load region (hereinafter referred to as a second high load operating state. In the present invention). In the first operation state), the oil supply amount from the center nozzles 41,... Is set to a predetermined supply amount (hereinafter referred to as a seventh supply amount, the first predetermined amount in the present invention), while the engine 1 When the operation state is a certain operation state in the low load region (hereinafter referred to as the second low load operation state, the second operation state in the present invention), the oil supply amount from the center nozzles 41,. The predetermined supply amount is smaller than the supply amount (hereinafter referred to as the eighth supply amount; the second predetermined amount referred to in the present invention) (see FIG. 7).

  In the lubricating device A of this embodiment, the amount of oil supplied from the center nozzles 41,... Is controlled as follows for the same reason as described above.

  That is, when the operating state of the engine 1 shifts from the second high load operating state to the second low load operating state, the PCM 50 reduces the oil supply amount from the center nozzles 41,. The amount is reduced from the eighth supply amount. As a result, immediately after the transition in which the amount of oil in the rotor housing 2 becomes excessive, the amount of oil supplied from the center nozzles 41 can be temporarily reduced, and oil consumption can be suppressed.

  Further, the PCM 50 increases the predetermined period as the difference between the seventh supply amount and the eighth supply amount increases. As a result, as the excess amount of oil in the rotor housing 2 increases, the period for temporarily reducing the oil supply amount immediately after the transition can be lengthened, and the oil consumption can be suppressed while satisfying the seal sound requirement. Can do.

  Further, when the cooling water temperature of the engine 1 detected by the cooling water temperature sensor 25 is equal to or lower than a predetermined temperature, the PCM 50 controls the amount of oil supplied from the center nozzles 41,. The oil supply amount is the same engine rotation state as the oil supply amount controlled according to the operating state of the engine 1 when the coolant temperature of the engine 1 detected by the coolant temperature sensor 25 is higher than the predetermined temperature. In the load state, the amount is increased. Thereby, it is possible to supplement the oil that has been washed away when the cooling water temperature of the engine 1 is low, and to prevent the seal members 16 to 18 of the rotor 6 from being worn.

  Furthermore, the PCM 50 is configured to decrease the increase value as the load of the engine 1 is lower. Thereby, oil consumption can be suppressed, satisfy | filling sealing performance request | requirement.

  The oil supply control flow will be described below with reference to the flowchart of FIG. 8 and also with reference to the time chart of FIG. FIG. 9 is a time chart showing an example of a time change of various states of the engine 1 when the operation state of the engine 1 is switched from the operation state in the high load region or the high rotation region to the operation state in the low load region or the low rotation region. (A) shows the time change of the engine load or engine speed, (b) shows the time change of the timer counter, (c) shows each nozzle 40,. , 41,..., 41,.

  First, in step S1, the intake air amount Q, the engine rotational speed Ne, and the coolant temperature Tw of the engine 1 are detected based on signals from the airflow sensor 23, the eccentric angle sensor 24, and the coolant temperature sensor 25. In the subsequent step S2, the engine load ce is calculated based on the intake air amount Q and the engine speed Ne.

  In step S3, it is determined whether or not the cooling water temperature Tw is equal to or lower than a predetermined water temperature T1 (see FIG. 10 described later). If the determination result in step S3 is NO and higher than the predetermined water temperature T1, the process proceeds to step S4. If the determination result is YES and equal to or less than the predetermined water temperature T1, the process proceeds to step S24.

  In step S4, it is determined whether or not the engine load ce is low. If the determination result in step S4 is NO and the load is high, the process proceeds to step S5. If the determination result is YES and the load is low, the process proceeds to step S8.

  In step S5, it is determined whether or not the engine speed Ne is low. When the determination result of step S4 is NO and high rotation, the process proceeds to step S6, while when the determination result is YES and low rotation, the process proceeds to step S16.

  In step S6, oil supply amounts from the nozzles 40,..., 41,... Are set from the normal control map on the basis of the engine speed Ne and engine load ce. The oil pumps 31 and 32 are driven and controlled, and the process returns to the start.

  On the other hand, in step S8, it is determined whether or not the previously calculated engine load ce was a high load. When the determination result in step S8 is YES and the previous high load (that is, when the engine load ce has shifted from a high load to a low load; see FIG. 9A), the process proceeds to step S9, while the determination result is If NO and the previous low load, the process proceeds to step S15.

  In step S9, the reduction flag is set to 1, and in the subsequent step S10, a time i for temporarily reducing the amount of oil supplied from each nozzle 40,..., 41,. (See FIG. 9B). This set time i is set according to the difference between the oil supply amount required at the time of the high load (see step S8) and the oil supply amount required at the time of the low load (see step S4). The larger the difference is, the longer it is.

  In step S11, it is determined whether or not the counter value is equal to or longer than the set time i. If the determination result in step S11 is NO and is smaller than the set time i, the process proceeds to step S12, while the determination result is YES and the set time i or more has been reached (that is, the predetermined period (see FIG. 9C)). When the time has elapsed), the process proceeds to step S13.

  In step S12, the oil supply amount from each nozzle 40,..., 41,... Is greater than the oil supply amount from each nozzle 40,. In step S7, the oil pumps 31 and 32 are driven and controlled based on the set amount, and the process returns to the start. Note that the weight loss value is previously set by examination or the like.

  In step S13, the counter for the set time i is reset, and in the subsequent step S14, the reduction flag is set to zero. In step S6, oil supply amounts from the nozzles 40,..., 41,... Are set from the normal control map, and in step S7, the oil pumps 31 and 32 are driven and controlled based on the set amounts. Return to the start.

  Further, in step S15, it is determined whether or not the weight reduction flag is 1. When the determination result in step S15 is YES and the reduction flag is 1, the process proceeds to step S10 to set a time i for temporarily reducing the oil supply amount from each of the nozzles 40,. When ce has not changed from the previous time, the set time i is left as it is.) In the subsequent step S11, it is determined whether or not the counter value has reached the set time i or more. On the other hand, if the decision result in the step S15 is NO and the reduction flag is 0, the process proceeds to a step S6 to set oil supply amounts from the nozzles 40,..., 41,. Then, the oil pumps 31 and 32 are driven and controlled based on the set amount, and the process returns to the start.

  On the other hand, in step S16, it is determined whether or not the previously detected engine speed Ne is high. When the determination result in step S16 is YES and the previous high rotation (that is, when the engine rotation speed Ne has shifted from high rotation to low rotation; see FIG. 9A), the process proceeds to step S17, while the determination result When NO is the last low rotation, the process proceeds to step S23.

  In step S17, the reduction flag is set to 1. In subsequent step S18, a time j for temporarily reducing the oil supply amount from each nozzle 40,..., 41,. (See FIG. 9B). This set time j is set according to the difference between the oil supply amount required at the time of the high rotation (see step S16) and the oil supply amount required at the time of the low load (see step S5). The larger the difference is, the longer it is.

  In step S19, it is determined whether or not the counter value is equal to or longer than the set time j. If the determination result in step S19 is NO and is smaller than the set time j, the process proceeds to step S20, while the determination result is YES and the set time j has been exceeded (that is, the predetermined period (see FIG. 9C)). When the time has elapsed), the process proceeds to step S21.

  In step S20, the oil supply amount from each nozzle 40,..., 41,... Is greater than the oil supply amount from each nozzle 40,. In step S7, the oil pumps 31 and 32 are driven and controlled based on the set amount, and the process returns to the start. Note that the weight loss value is previously set by examination or the like.

  In step S21, the counter of the set time j is reset, and in the subsequent step S22, the reduction flag is set to zero. In step S6, oil supply amounts from the nozzles 40,..., 41,... Are set from the normal control map, and in step S7, the oil pumps 31 and 32 are driven and controlled based on the set amounts. Return to the start.

  Further, in step S23, it is determined whether or not the weight reduction flag is 1. If the decision result in the step S23 is YES and the reduction flag is 1, the process proceeds to a step S10 to set a time j for temporarily reducing the oil supply amount from the nozzles 40,. When the speed Ne has not changed from the previous time, the set time j is set as it is.) In the subsequent step S11, it is determined whether or not the counter value is equal to or greater than the set time j. On the other hand, if the decision result in the step S15 is NO and the reduction flag is 0, the process proceeds to a step S6 to set oil supply amounts from the nozzles 40,..., 41,. Then, the oil pumps 31 and 32 are driven and controlled based on the set amount, and the process returns to the start.

  In step S24, the oil supply amount from each nozzle 40, ..., 41, ... is set according to the cooling water temperature Tw. Specifically, the oil supply amount is determined based on the oil supply amount from the nozzles 40,..., 41,... Set from the normal control map when the cooling water temperature Tw is higher than the predetermined water temperature T1 (the step Rather than S6), the amount of increase is set in the same engine rotation state and load state. This increase value is made smaller as the engine load ce is lower. FIG. 10 is a graph showing an example of the relationship between the cooling water temperature Tw and the increase value when the cooling water temperature Tw is equal to or lower than the predetermined temperature T1, and the solid line in FIG. 10 indicates when the engine load ce is low. The relationship between the two is shown, and the broken line shows the relationship between the two at high load. In the example of this figure, until the cooling water temperature Tw becomes equal to or lower than the predetermined temperature T2, the increasing value increases in proportion to the cooling water temperature Tw. On the other hand, when the cooling water temperature Tw becomes lower than the predetermined temperature T2, the increasing value increases. Is a constant value. In step S7, the oil pumps 31 and 32 are driven and controlled based on the oil supply amount set in step S24, and the process returns to the start.

(Other embodiments)
In addition, the structure of this invention is not limited to the thing of above-described embodiment, Other various structures are included. That is, in the above embodiment, the oil supply ratio from the side nozzles 40,... (Ratio to the oil supply amount from the center nozzles 41,. However, the present invention is not limited to this, and the amount of oil supplied from the side nozzles 40,... And the center nozzles 41,.

  In the above embodiment, the two oil pumps 31 and 32 are arranged in parallel in the moving direction of the rotor 6 above the engine 1 so that the oil flows upward. The layout is merely an example, the layout is free, and it is not necessary to use the two oil pumps 31 and 32.

  Furthermore, the rotary piston engine 1 to which the lubricating device of the invention is applied is not limited to the one in which the exhaust ports 15 and 22 are opened on both sides of the working chamber 5 as in the above embodiment, and the exhaust port is only on one side. May be opened. In this case, the side nozzles 40,... May be only on one side where the exhaust port is opened, but the center nozzles 41,. It can be said that it is preferable to arrange the side nozzles 40,..., Because substantially uniform lubrication is possible from the outer periphery to the side portion of the rotor 6.

  Furthermore, in the above-described embodiment, the amount of oil supplied from the center supply port 2b and the side supply port 2c is controlled to decrease for a predetermined period from the transition of the operating state of the engine 1, but this is not limitative. Instead, for example, either one of the oil supply amounts from the center supply port 2b and the side supply port 2c may be controlled to decrease, and the total oil supply amount from the center supply port 2b and the side supply port 2c may be controlled. May be controlled to reduce the amount.

  The present invention is not limited to the embodiments, and can be implemented in various other forms without departing from the spirit or main features thereof.

  As described above, the above-described embodiment is merely an example in all respects and should not be interpreted in a limited manner. The scope of the present invention is defined by the claims, and is not limited by the specification. Further, all modifications and changes belonging to the equivalent scope of the claims are within the scope of the present invention.

  As described above, the lubrication device for a rotary piston engine according to the present invention can be applied to applications that require oil consumption to be suppressed.

It is sectional drawing which shows the principal part structure of the rotary piston engine which concerns on embodiment of this invention. It is a whole block diagram of the lubricating device of the engine. It is a figure which shows the lubricating device on the engine main body by planar view. FIG. 4 is a cross-sectional view taken along line IV-IV in FIG. 1 showing a layout of the oil supply nozzle. FIG. 5 is a cross-sectional view taken along line V-V in FIG. 1 showing the structure of the metering oil pump. It is explanatory drawing which shows the change of the lubrication request | requirement of a gas seal part matched with the driving | operation area | region of an engine. It is explanatory drawing which shows an example of the map of oil supply control. It is a flowchart figure which shows oil supply control. It is a time chart which shows an example of the time change of the various states of an engine when the operation state of an engine switches from the operation state in a high load region or a high rotation region to the operation state in a low load region or a low rotation region, (a ) Shows the time change of the engine load or the engine rotation speed, (b) shows the time change of the timer counter, and (c) shows the time change of the oil supply amount from the nozzle. Is. It is a graph which shows an example of the relationship between the cooling water temperature of an engine, and the increase value of oil supply amount when an engine cooling water temperature is below predetermined temperature.

A Lubricating device 1 Rotary piston engine 2 Rotor housing 2a Trochoid inner peripheral surface 2b Center supply port 2c Side supply port 25 Cooling water temperature sensor (cooling water temperature detecting means)
3 Side housing, Intermediate housing 50 Controller (PCM: Control means)

Claims (6)

A lubrication device for a rotary piston engine that supplies oil from a supply port that opens to the inner peripheral surface of a trochoid of a rotor housing,
Comprising control means for controlling the amount of oil supplied from the supply port in accordance with the operating state of the engine;
The control means sets the oil supply amount to a first predetermined amount when the operating state of the engine is in the first operating state, and reduces the oil supply amount when the engine operating state is in the second operating state. When the engine operating state shifts from the first operating state to the second operating state, the oil supply amount is changed to the second predetermined amount that is less than the first predetermined amount. 2. A lubricating device for a rotary piston engine, wherein the lubricating device is configured to reduce the amount from a predetermined amount. The rotary piston engine lubrication device according to claim 1,
The lubrication device for a rotary piston engine, wherein the first operation state is an operation state in a high rotation region, and the second operation state is an operation state in a low rotation region. The rotary piston engine lubrication device according to claim 1,
The first operating state is an operating state in a high load region, while the second operating state is an operating state in a low load region. The lubricating device for a rotary piston engine according to claim 2 or 3,
The lubricating device for a rotary piston engine, wherein the control means is configured to lengthen the predetermined period as a difference between the first predetermined amount and the second predetermined amount is larger. The lubricating device for a rotary piston engine according to claim 2 or 3,
A cooling water temperature detecting means for detecting a cooling water temperature of the engine;
The control means controls the oil supply amount according to the cooling water temperature when the cooling water temperature detected by the cooling water temperature detection means is equal to or lower than a predetermined temperature, and the oil supply amount is set to the cooling water temperature. When the coolant temperature detected by the temperature detection means is higher than the predetermined temperature, the oil supply amount is controlled in accordance with the operating state of the engine and is increased in the same rotational state and load state. A lubrication device for a rotary piston engine. The rotary piston engine lubrication device according to claim 5,
The said control means is comprised so that the said increase value may be made small, so that the load of the said engine is low, The lubrication apparatus of the rotary piston engine characterized by the above-mentioned.

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