JPH0625531B2 - Internal combustion engine - Google Patents

Description

The present invention relates to internal combustion engines.

Perlewitz, US Patent No. 2,935,057, issued May 30, 1960, Sp, issued December 2, 1969.
arrow no. 3,481,318, April 4, 1972
Leitermann, Issue 3,653,684, 19 issued daily
Shaver, No. 3,913,5, issued October 21, 1975.
No. 51, Issue 4 of Schreier, March 6, 1979.
No. 142,486, Beat, issued December 16, 1924
See ibid., 1,519,478.

Conventionally, in this type of internal combustion engine, for example, Japanese Utility Model Publication No. 43-23
As shown in 606, a crankcase and a pump are provided, a movable wall is provided in the housing of the pump to divide the housing into two chambers, and these chambers and the crankcase are connected to each other. A pump has been used in which pressure fluctuations are guided to the chambers so that the movable wall reciprocates.

However, in such a conventional pump, one chamber is connected to the first crankcase and the other chamber is connected to the second crankcase, and the pressure relationship between these crankcases is such that one is the maximum pressure. At this time, since the other is in the relationship of having the minimum pressure, the rotational speed of the pump becomes equal to the rotational speed of the internal combustion engine, so the pump is driven at a very high rotational speed, which is not preferable in terms of durability. There was a problem. Further, since two or more crankcases are required, there is a problem in that it cannot be used for a single cylinder engine having only one crankcase.

The present invention has been made in view of the problems of the prior art, and an object of the present invention is to provide an internal combustion engine having a pressure-operated motor that is excellent in durability and is not limited by the number of crankcases, that is, the number of cylinders. .

Thus, in the present invention, at least one crankcase (67) and at least one pressure actuated motor (13).
The crankcase (67) is under relatively high and low pressure conditions, the pressure conditions having a frequency and amplitude that vary according to changes in engine speed. Alternating with each other, the pressure actuated motor (13)
Comprises a housing (15), a movable wall (121) and a device (140) for reciprocating the movable wall (121), the movable wall (121) being arranged in the housing, The housing is divided into a low pressure chamber (123) and a high pressure chamber (125) whose volumes alternately change in opposite directions, and the device (140) has a frequency lower than a frequency of a pressure cycle of the crankcase. The movable wall is reciprocated with a stroke having, and the device (140) comprises means (151) for connecting the low pressure chamber and the high pressure chamber to one crankcase, According to an aspect of the present invention, there is provided a structure in which a pressure difference is generated between the low pressure chamber and the high pressure chamber, and the movable wall is movable in one direction. Is shall.

Other features and advantages of each embodiment of the invention include:
It will be apparent from a comparison of the following general description, claims and drawings.

Before describing one embodiment of the present invention in detail, it should be understood that the present invention is not limited in its application to the details of construction and structure shown in the following description and drawings. The invention is capable of other embodiments and of being practiced in various ways. It should also be understood that the phraseology used in this text is for the purpose of description and should not be regarded as limiting.

Shown in the drawing is a marine propulsion unit in the form of an outboard motor 3, which is equipped with a power head 7 containing a two-stroke internal combustion engine 8 and fixed to the power head 7. It includes a lower device 9 for rotatably supporting a propeller 10 driven by an internal combustion engine 8.

For the internal combustion engine 8, a fluid pressure operated motor 13 operated by a supply source that alternately provides high pressure and low pressure, respectively.
A combined fuel / oil pump 11 including is coupled.

Further, the fuel / oil pump 11 includes a housing 15,
In addition to the fluid pressure actuated motor 13, an oil pump device 17
And a fuel pump device 19.

Furthermore, the housing 15 includes a peripheral wall 21, a top wall 23, an intermediate wall or partition 25, a bottom wall 27 and a downward extension 29. The intermediate wall 25 includes a central inner bore or port 31 to connect the housing 15 to the upper compartment 3.
3 and a lower compartment 35.

The fuel pump device 19 is arranged in the lower compartment 35. The fuel pump device has a reciprocating member 39 which defines a variable volume fuel pump chamber 45 between the member 39 and the bottom wall 27.
And a lower chamber, that is, a ventilation chamber 47, which communicates with the atmosphere through a port 49. A flexible diaphragm or diaphragm 43 is attached to the member 39 around the member 39, and these are attached to the fuel pump piston 4.
Make up one. The diaphragm 43 is further attached to the peripheral wall 21 of the housing 15.

The fuel pump chamber 19 also has a conduit 5 at the peripheral wall 21.
A fuel supply chamber 55 for communicating with a suitable fuel supply source 55 and allowing fuel to flow in and preventing fuel from flowing out of the fuel pump chamber 45 in response to an increase in the volume of the fuel pump chamber 45. It includes a fuel inlet portion 51 having a directional acting check valve device 57.

The fuel pump device 19 also includes a device such as a carburetor 65 and a line 63 for supplying the fuel / oil mixture to the crankcase 67 of the two-stroke internal combustion engine 8 at the peripheral wall 21.
Fuel outlet 61 with valve adapted to communicate via
Is included. The valved fuel outlet portion 61 includes a one-way check valve device 71 that permits fuel outflow and blocks fuel inflow in response to a decrease in volume in the fuel pump chamber 45.

The conduit 63 preferably includes an accumulator 75 in the form of a cylinder 77 which communicates with this conduit 63 at one end and vents to the atmosphere at the other end by a port 79. A piston 81 is arranged inside the cylinder 77, and the piston 81 has a volume variable storage chamber 8 by a spring 83.
5 is suitably biased toward line 63 to provide 5, but said storage chamber 85 acts to reduce or eliminate fuel pulsation at the outlet end of line 63. To do.

The oil pump device 17 is disposed in the lower extension portion 29 and includes a cylindrical space 87 extending in a substantially aligned position with the central port 31 of the intermediate wall 25 and extending from the ventilation chamber 47. There is. Inside the cylindrical space 87,
A fuel pump piston 41 which reciprocates in a space 87 and partially defines a variable volume oil pump chamber 93.
There is a reciprocable element or oil pump plunger 91 which is preferably integrally extended from the.
Oil pump plunger or element 91 and cylindrical space 87
A sealing device 95 is provided between the wall surface and the wall surface.

The oil pump chamber 17 is also connected to the oil supply source 1 via the line 103.
And an inlet portion 101 having a one-way check valve 107 in communication with 05 and allowing oil inflow and blocking oil outflow in response to an increase in the volume of the oil pump chamber 93.

The oil pump device 17 also includes a valved outlet section 111. In the illustrated structure, this outlet 111 allows oil to pass through the fuel pump chamber 4 although various other configurations may be used.
5 is configured to be sent. Further, the outlet portion 111 includes an inner hole 113 extending in the axial direction inside the oil pump / plunger 91, the inner hole communicating with the oil pump chamber 93 at one end, and the fuel at the other end. Oil is supplied to the fuel pump chamber 45 in response to a decrease in the volume of the oil pump chamber 93, including one or more radial branch ports 115 communicating with the pump chamber 45 and intermediate the inlet portion 101 and the outlet portion 111. One-way check valve device 1 that allows the outflow but prevents the inflow of oil into the oil pump chamber 93.
It includes an enlarged central portion 117 having 19.

The fluid pressure actuated motor 13 is located generally in the upper compartment 33 and is coupled to the oil pump plunger 91 and the fuel pump piston 41 to produce its common reciprocating motion over a stroke or distance. Further, the fluid pressure actuated motor 13 is responsive to a source of alternating high pressure and low pressure to respond to the fuel pump piston 41 and the oil pump plunger in a cycle shorter than an alternating cycle of relatively high and low pressure. 91 reciprocating motions occur.
Furthermore, the fluid pressure operated motor 13 has a relatively low pressure variable volume chamber or low pressure chamber 123 above the upper compartment 33.
And a lower movable wall 121 which divides into a relatively high pressure variable volume chamber or high pressure chamber 125. This movable wall 121 is a piston at the center, that is, the motor piston 1.
27, which is fixed at its outer periphery to the peripheral wall 21 so as to divide the upper compartment 33 into the aforementioned relatively low pressure chamber and relatively high pressure chamber.

The internal combustion engine 8 also comprises a device 140 for reciprocating the movable wall 121 with a stroke having a frequency which is lower than or different from the crankcase pressure cycle frequency. In the disclosed structure, as will be described in more detail below, such a device 140 includes a port 191 provided in the movable wall 121,
A valve member 1 that is movable with respect to the position where the port 191 is closed
93, a spring 141 that urges the movable wall 121 in a direction that minimizes the volume of the high pressure chamber 125, and a pressure difference between the high pressure chamber 125 and the low pressure chamber 123, thereby generating the low pressure chamber. A device 151 that connects the crankcase 67 to the low pressure chamber 123 and the high pressure chamber 125 is provided so that the movable wall can be moved in a direction that minimizes the volume of the 123.

Fuel pump piston 41 and oil pump plunger 9 so that motor piston 127 also moves with it.
It is desirable to be integrally connected with 1. From what has just been said, the combined motor piston 127, fuel pump piston 41 and oil pump plunger 91.
Defines a central portion 131 that extends from the piston 41 through a central bore or port 31 in the intermediate wall 25 toward the motor piston 127 and an open valve cage 135 and which is central to the motor. And a coupling part for coupling to the piston 127. Suitable seal 139
Is provided between the intermediate wall 25 and the central portion 131.

The fluid pressure actuated motor 13 further includes a device for biasing the movable wall 121 to displace the movable wall 121 in a direction that minimizes the volume of the high pressure chamber 125 and maximizes the volume of the low pressure chamber 123. There is. In the configuration shown, such a device has a top wall 23 at one end.
And the motor piston 12 at the other end.
7 includes a coil spring 141 that abuts against 7.

The fluid pressure actuated motor 13 is also between the low pressure chamber 123 and the high pressure chamber 125 to displace the movable wall 121 in a direction that minimizes the volume of the low pressure chamber 123 and maximizes the volume of the high pressure chamber 125. Each includes a device 151 for creating a pressure difference. Although various configurations are available, in the configuration shown, the device couples to a source of alternating higher and lower pressures, thus allowing outflow from the lower pressure chamber 123. A device including a device for blocking inflow to the low pressure chamber 123;
Included is a device that allows inflow to high pressure chamber 125 and blocks outflow from high pressure chamber 125.

It is desirable that the supply source for alternately supplying a relatively high pressure and a low pressure is the crankcase 67 of the two-stroke internal combustion engine 8. However, other sources of relatively high and low pressure are also applicable. Furthermore, relatively high and low pressures mean two positive pressures above atmospheric pressure, or two negative pressures below atmospheric pressure, or one positive pressure above atmospheric pressure and one below atmospheric pressure. It means negative pressure.

Furthermore, said device 151 for creating a pressure difference between relatively low pressure chamber 123 and relatively high pressure chamber 125.
Is also a line arrangement 161 including a main line 163 to be coupled to alternating high and low pressure sources such as the crankcase 67 of the two-stroke internal combustion engine 8, the low pressure chamber 123 and the main line. A first or low pressure branch line 165 communicating with the high pressure chamber and the main line 163.
A second or high pressure branch line 167 communicating between
Includes and.

The low pressure branch line 165 includes a one-way check valve 169 that allows outflow from the low pressure chamber 123 and blocks inflow to the low pressure chamber 123. A one-way check valve 171 that allows the flow to the high pressure chamber 125 and blocks the outflow from the high pressure chamber 125 is disposed in the high pressure branch line 167.

Thus, the alternating pulsations of relatively high and low pressures present in the main line 163 cause relatively high pressures in the high pressure chamber 125 and relatively low pressures in the low pressure chamber 123, This pressure difference is due to the biasing spring 14 of the movable wall.
The pressure difference is sufficiently large as compared with the biasing action of 1. Therefore, this pressure difference moves from the position where the high pressure chamber 125 has the minimum volume to the position where the low pressure chamber 123 has the minimum volume to move the movable wall 121. Is effective in producing

The line device 161 also preferably includes a device for relieving excessive pressure differentials. From this point, the pipe line device 161 is in direct communication with the low pressure chamber 123 and the high pressure chamber 125, respectively, so that the low pressure branch pipe line 165 and the high pressure branch pipe line 167 are respectively connected to the bypass pipe line 175.
Is included. The bypass line 175 includes a ball member 179 that is normally engaged with the seal 181, and a spring 183 that is configured to release the ball member 179 from the seal 181 in the event of an excessive pressure differential. Pressure relief valve 177 of FIG.

The fluid pressure actuated motors 13 also each have a low pressure chamber 1
In response to the movement of the motor / piston which minimizes the volume of 23, a communication state is established between the low pressure chamber 123 and the high pressure chamber 125, which results in a pressure difference between the low pressure chamber 123 and the high pressure chamber 125. Of the movable wall 121 by means of the biasing spring 141 in a direction that minimizes or minimizes the volume of the high pressure chamber 125 and maximizes the volume of the low pressure chamber 123. . Such a device is provided, at least in part, by a conduit line (not shown) that bypasses the motor piston 127 in the illustrated configuration, such a device including a combined motor piston 127 and fuel pump. It comprises a piston 41 and a valve member 193 located in the open cage 135 of the oil pump plunger 91 and movable between a closed position and an open position, and a central port 191 of the motor piston 127. The valve member 193 is received downward in an engaging recess or axial bore 197 in the central portion 131 of the fuel pump piston which is combined to guide its movement between its open and closed positions. It is desirable to include an extending stem 195.

In addition, the device, which creates a communication between the respective low pressure chamber 123 and high pressure chamber 125, has a valve member 193 in the open position.
It includes a spiral spring 201 for pressing. This spring 201 has a top wall 2 of the housing 15 at one end.
3 and a motor piston 127 at the other end
Extends through the central port 191 and abuts the upper surface of the valve member 193. The bias spring 201 of this valve member is
The valve member 193 is displaced toward the open position when the motor piston 127 approaches a position that minimizes the volume of the low pressure chamber 123 by overcoming the pressure differential between the low pressure chamber 123 and the high pressure chamber 125, respectively. It is configured to be able to act.

The motor to the position where the volume of the low pressure chamber 123 is minimized.
A device is also provided to ensure complete opening movement of the valve member 193 in response to the approach of the piston 127. Such a device is provided in the low pressure chamber 123 and defines an intermediate chamber 211 which communicates with the central port 191 to allow the first opening of the valve member 193 and the outflow from this intermediate chamber 211 to the low pressure chamber 123. A device is included to reduce the pressure differential between the high pressure chamber 125 and the intermediate chamber 211 by creating resistance and thereby induce movement of the valve member 193 to the fully open position. Such movement substantially reduces the pressure differential between the low pressure chamber 123 and the high pressure chamber 125, thereby causing the volume of the high pressure chamber 125 to be minimized by the action of the biasing spring 141 of the motor piston. 121 movements are allowed. Various configurations can be used, but in the configuration shown, such a device is provided inside the low pressure chamber 123,
Inside the lower pressure chamber 123 from the top wall 23 of the housing 15 is an annular flange or ring 213 that extends radially outside of the valve member bias spring 201 and radially inside of the motor piston bias spring 141. Further, such a device may include a motor piston 127 to the top wall 23.
At the end of the stroke to minimize the volume of the low pressure chamber 123 so as to resist the flow from the intermediate chamber 211 toward the low pressure chamber 123. It also includes a cooperating annular flange or ring 215 that is movable in a telescoping position relative to the flange or ring 213 as the piston 127 approaches.

Such resistance to the flow between the intermediate chamber 211 and the low pressure chamber 123 is due to the high pressure chamber 125 and the intermediate chamber 21.
1, resulting in a reduced pressure differential between the valve member 19 and the valve member 19
This ensures the action of the biasing spring 201 of the valve member which causes the displacement of 3 to its fully open position.

The fluid pressure actuated motor 13 is also responsive to piston movement that minimizes the volume of the high pressure chamber 125 to interrupt communication between the low pressure chamber 123 and the high pressure chamber 125, respectively, thereby creating a fluid pressure differential. Lower pressure chamber by device 1
Also included is a device that allows the formation of a fluid pressure differential between 23 and the high pressure chamber 125, thereby causing displacement of the motor piston 127 in a direction that maximizes the volume of the low pressure chamber 125. In the structure shown, the device is of the motor piston 1 type, although other configurations are also possible.
When the valve 27 approaches a position that minimizes the volume of the high pressure chamber 125, the valve cage 135 opens upward from the intermediate wall 25.
Through the valve member 193 toward the valve member 193
3 comprises a plurality of studs or posts 221 for placing 3 in the closed position.

Thus, in operation, the high pressure and the low pressure in the conduit device 161 are alternately present (valve member 19
3 in the closed position), a relatively high pressure in the relatively high pressure chamber 125 is created and maintained,
Further, at the low pressure 123, the pressure is reduced to a low pressure and this state is maintained. The pressure difference thus generated opposes the action of the biasing spring 141 of the motor piston to the position where the volume of the low pressure chamber 123 is minimized.
The displacement of the movable wall 121 including 27 will occur. As the motor piston 127 approaches a position that minimizes the volume of the low pressure chamber 123, the biasing spring 201 causes the displacement of the valve member 193 to open the port 191 of the motor piston to the open position, thereby reducing the pressure differential. The action of the biasing spring 141 acts to allow the displacement action of the movable wall 121 to a position that reduces or minimizes and also minimizes the volume of the high pressure chamber 125. During such movement, if there is no pressure difference, the valve member 193 will move the biasing spring 20.
The open position is maintained under the action of 1.

Upon approaching the movable wall 121 containing the motor piston 127 to a position that minimizes the volume of the high pressure chamber 125, the stud 221 engages the valve member 193 to cause its movement to its closed position. When the central port 191 is thereby closed, a pressure differential is created again and the movable wall 121 is again displaced in the opposite direction to start another operating cycle. When the fuel pump piston 41 and the oil pump plunger 91 perform common motion with the motor piston 127, the fluid pressure actuated motor 13 causes the reciprocating motion of these components to be shorter than the period in which the fluid pressure actuated motor 13 is energized. It will also occur in cycles, i.e. in cycles shorter than the alternating high and low pressure rates in the source.

It is desirable to provide a device for selectively adjusting the discharge amount of the oil pump device 17 regardless of the displacement amount of the oil pump / plunger 91 in a substantially constant stroke. In the construction shown, the device has a subchamber 231 extending from the oil pump chamber 93 and containing a floating piston 233 therein, although many other configurations can be used. A suitable seal 2 is provided between the floating piston 233 and the wall surface of the sub chamber 231.
35 are provided. The floating piston 233 has, at its outer end, a suitable link device 241 which extends outside the subchamber 231 and is shown in dotted lines to the throttle 243 of the engine.
Has a portion 237 that is engaged by a cam 239 that is coupled by means of and is positionable in response to the selective positioning of the engine throttle 243. Therefore, the cam 239 variably limits the outward movement of the floating piston 233, thereby controlling the effective pumping stroke of the oil pump plunger 91.

The combined fuel / oil pump 11 has a crankcase 67
Can be connected to the block of the two-stroke internal combustion engine 8 in direct connection with and to a remote source of oil and fuel. Alternatively, if desired, the fuel / pump 11 may be located at a remote location more or less close to the fuel and oil sources, or in conjunction therewith, and a conduit (not shown). ) Can be extended between the fuel / oil pump 11 and the crankcase 67 or a supply source for alternately supplying high pressure and low pressure.

Shown in FIG. 2 is another embodiment of a fuel / oil pump 301 according to the present invention. The structure shown in FIG. 2 is substantially the same as that shown in FIG. 1, except for a device for ensuring the complete opening of the valve member 193, a device for changing the oil flow rate and an oil discharge device. Therefore, the same reference numerals are attached to similar components.

In the configuration shown in FIG. 2, the ring is associated with a device that ensures complete opening movement of the valve member 193 in response to the motor piston 127 approaching a position that minimizes the volume of the low pressure chamber 123. 213 and 215 are omitted, so that the intermediate chamber 211 does not exist. Instead, a fixed member or column 302 is provided that depends downwardly from the top wall 23 at a position where it engages the valve member 193 when the movable wall 121 minimizes the volume of the low pressure chamber 123. Such engagement results in a "rip" or slight opening in the central port 191, thus slightly reducing the pressure differential across the moveable wall 121. Such a reduction in pressure difference immediately facilitates the action of the poppet valve member biasing spring 201 to displace the valve member 193 to fully open the central port 191 and thereby substantially reduce the pressure difference. And the movement of the movable wall in the direction that minimizes the high volume of the pressure chamber 125 under the action of the movable wall biasing spring 141. It can also be seen that the column 302 acts to stabilize or position the upper end of the bias spring 201 of the poppet valve member.

In the embodiment shown in FIG. 2, the oil pump device is
It includes an oil pump piston 303 which partially defines a variable volume oil pump chamber 393. The oil pump / piston 303 is slidably engaged with the oil pump / plunger 91 by an upper end portion of the piston 303 arranged in a closed chamber 307 at the center of the oil pump / plunger 91. The intermediate portion 309 of the oil pump piston 303 extends to the outside of the chamber 307 through the opening 311 and
The upper end 305 of the piston 303 is joined to the lower part 313 of the cylindrical space 87. Since the upper end 305 of the oil pump piston 303 is larger than the opening 311, the oil pump piston 303 moves together with the oil pump plunger 91 when the oil pump plunger 91 moves upward. Above the lower end 317 of the oil pump piston 303, a sealing device 315 is provided between the lower part 313 of the piston and the wall of the space 87. This position of the sealing device 315 is defined by the valve inlet 101 and outlet 319.
Allows the lower end 317 of the piston to extend below.

In the present embodiment, the oil pump device 17 includes the inlet portion 10
1 includes a valved outlet 319 that extends concentrically to the opposite side of the space 87. The outlet portion 319 includes a one-way check valve 321 to allow the oil to flow to the line 63 for supplying the oil to the carburetor 65.

In the embodiment shown in FIG. 2, the device for selectively adjusting the discharge amount of the oil pump device is the oil pump chamber 39.
3 includes an adjustable stop 323 that partially defines 3. The adjustable stopper 323 is provided on the inlet 101
And is disposed in the space 87 below the outlet 319.
A suitable seal 325 is provided between the stopper 323 and the wall of the space 87, and the adjustable stopper portion 327 above the seal 325 has a diameter smaller than the diameter of the space 87 and is the adjustable stopper portion. 327 is the entrance 1
01 and extend above the outlet 319.
The lower end of the stopper 323 includes a portion 329 extending outside the space 87 and engaged by the cam 239. The cam 239 operates as described above.

The oil pump device also includes a device for biasing the oil pump piston 303 toward the stopper 323. This biasing device comprises a spring 33 between the upper end 305 of the piston and the oil pump plunger 91 in the central chamber 307.
It is 1.

In operation, as the oil pump plunger 91 moves downward, the oil pump piston 303 moves downward an equal distance. The biasing device or spring 331 is preloaded so that it does not deflect due to oil pump pressure or seal friction. When the oil pump piston 303 moves downward, the volume of the variable-volume oil pump chamber 393 decreases, and the oil is forcibly discharged through the outlet 319. However, the oil pump / piston 303 has a stopper 32.
When in contact with 3, the piston does not move anymore and the remaining stroke of the movable element 91 is the biasing device or spring 33.
Lost by flexing 1. Therefore, the position of the stopper 323 changes the volume of the variable-volume oil pump chamber 393 and the amount of oil supplied by the pump device.

FIG. 3 shows another embodiment of a combined fuel / oil pump 401 embodying features of the present invention in connection with internal combustion engine 8. The structure shown in FIG. 3 is substantially the same as the structure shown in FIG. 2, with a slight modification of the fuel pump device such that the oil pump device has movable parts 239 or elements 323.
And the motor piston 1 without the associated linkage and modified to produce a change in the output of the oil pump according to the speed of the engine, and without the one-way pressure regulating valve 177.
The 27 strokes differ in that they vary according to engine speed, but the same reference numbers are used for the same components. With respect to the last-mentioned point, the poppet valve bias spring 201 acts to open the central port 191 before the full stroke of the motor piston 127 while the internal combustion engine 8 is operating at low speed, and the internal combustion engine 8 is at high speed. Has a spring constant that acts to open the central port 191 upon completion of the full stroke of the motor piston 127 during operation.

Further, as is well known, in a two stroke engine, the movement of the piston relative to the cylinder and crankcase 67 is
It acts to create a relatively high and low cyclical condition within the crankcase that defines the magnitude of the crankcase pressure that varies with engine speed, ie, increases with engine speed. For example, when the engine is idling, the pressure inside the crankcase is
About +0.211 to -0.211kg / cm ² (About +3 to -3ps
It can vary in the range of i). Also, for example, when operating at high engine speed, the pressure inside the crankcase is approximately +0.35
2 to -0.422 kg / cm ² (+5 to -6 psi) or about +0.703 to -0.070 kg / cm ² (+10 to -1 psi)
Of about 0.773 kg / cm ² (11 ps)
This produces a crankcase pressure of the magnitude i).

Under operating conditions, the pressure in the low pressure chamber 123 and the high pressure chamber 125 of the crankcase 67, and the pressure in the low pressure chamber 123 and the high pressure chamber 125, respectively, are coupled, so The conditions rapidly reflect the pressure inside the crankcase 67, and the pressure difference between the both ends of the operable motor piston 127, that is, the low pressure chamber 123 and the high pressure chamber 1, respectively.
A pressure difference of between 25 is produced, which has a magnitude approximating that of the crankcase pressure.

As mentioned above, the poppet valve biasing spring 201 causes the partial movement of the motor piston 127 between the positions of the low pressure chamber 123 and the high pressure chamber 125, which results in the smallest volume, respectively.
It has a spring constant such that it produces a compressed state of the poppet valve bias spring 201 so as to overcome the acting force on the valve member 193 in response to the pressure difference when the internal combustion engine 8 operates at a low speed. However, this spring constant is such that, whenever the internal combustion engine 8 is operated at high speed, the acting force generated by the pressure difference causes a relatively large movement of the movable wall 121 or the motor piston 127 prior to the opening operation of the central port 191. Volume, that is, large enough to produce the total stroke volume. As a result, the motor piston 127 is provided with a stroke that varies with engine speed, i.e., a stroke that increases in length with engine speed.

In the fuel pump device used in the engine shown in FIG. 3, the valved fuel inlet portion 51 has a lower chamber 47 (of course,
It is different from that shown in FIG. 1 and FIG. 2 by making it communicate with (non-ventilated state). Further, the movable wall 39 is provided with one or more openings 411, each of which is unidirectional to allow the flow from the lower chamber 47 to the upper chamber 45 and prevent the flow from the upper chamber 45 to the lower chamber 47. The check valve member 413 is provided. The stroke of the fuel pump member or movable wall 39 is the same as the stroke of the motor piston 127, so that the amount of fuel delivered will vary with engine speed, ie will increase with increasing engine speed.

If desired, the same fuel pump construction as shown in FIGS. 1 and 2 may be used.

In the oil pump device of this embodiment, the amount of oil supplied is automatically changed according to the engine speed, and
Due to the aerodynamic coupling relationship between the piston 127 and the oil pump / piston 303, the oil pumping action can be intermediate between low speed and high speed, and also increases with engine speed increasing above this first engine speed level. It differs from the structure shown in FIGS. 1 and 2 in that it does not occur until the first engine speed level is reached.

In regard to the point just mentioned, the oil pump piston 303 is coupled to the motor piston 127 to cause movement therewith in one part of the stroke of the motor piston, and in another part of the stroke of the motor piston 127. Produce an aerodynamic movement in. In this regard, the oil pump / piston 3
03 is provided at its upper end with an axial recess or bore 415 defined by an inner annular flange 417 which defines an opening 419 at its upper end.
The piston 127 is provided with an extension 421 penetrating the opening 419 provided by the annular flange 417, and the lower end of the extension 421 has an annular flange 4
It includes an enlarged head 423 that cannot pass through the opening 419 defined by 17. Thus, the high pressure chamber 125
Motor piston 127 from a position that minimizes the volume of
The first ascending stroke movement of the oil pump piston 313 does not occur. However, before the motor piston 127 reaches the position where the volume of the low pressure chamber 123 is minimized, the head 423 engages the annular flange 417 to move the oil pump piston 303 with the motor piston 127. Cause. The first down stroke movement of the motor piston 127 does not result in movement of the oil pump plunger until the blind end of the recess or bore 415 and the enlarged head 423 are engaged. Thus, the oil pump action is
It occurs only at the top of the upstroke of the motor piston movement and at the bottom of the downstroke of the motor piston movement. Thus, the oil pumping system shown in FIG. 3 produces little or no pumping action at low engine speeds, and the oil pumping action increases with increasing speed above the lower engine speeds.

As in the configuration shown in FIG. 2, the oil discharge from outlet 319 is transmitted to fuel supply conduit 63 for mixing with fuel. However, if desired, the supplied oil can be transferred to mix with the fuel in the upper chamber 45 or the lower chamber 47.

As described above, according to the present invention, since the movable wall of the pressure actuating motor is reciprocated with the stroke having a frequency lower than the frequency of the pressure cycle of the crankcase, the rotational speed lower than the rotational speed of the internal combustion engine is achieved. Since the pressure actuated motor is operated in a number, the durability can be greatly improved as compared with the prior art.

Also, when the speed of the internal combustion engine increases, the pressure difference that occurs in the crankcase (the difference between the high pressure state and the low pressure state)
Is increased and the movement of the movable wall is accelerated, so that the proportion of oil or fuel supplied to the internal combustion engine by the pressure-operated motor can be changed according to the rotational speed of the internal combustion engine.

Further, since one crankcase is connected to the low pressure chamber and the high pressure chamber of the pressure-operated motor and a pressure difference is generated between these chambers so that the movable wall reciprocates, the crankcase is not moved. Since it can also be used in a single-cylinder internal combustion engine having only one cylinder, there is an effect that it can be used regardless of the number of cylinders.

[Brief description of drawings]

1 is a schematic view showing an embodiment of a combined fuel / oil pump including a fluid pressure operated motor, FIG. 2 is a schematic view showing another embodiment of a fuel / oil pump including a fluid pressure operated motor, And FIG. 3 is a schematic diagram showing yet another embodiment of a fuel / oil pump including a fluid pressure operated motor. 3: Outboard motor, 7: Power head, 8: Internal combustion engine, 9: Lower device, 10: Propeller, 11: Fuel / oil pump, 13: Fluid pressure operated motor, 15: Housing, 17: Oil pump device, 19 : Fuel pump device, 21: peripheral wall, 23: top wall, 25: middle wall, 27: bottom wall, 29: downward extension part, 31: port, 33: upper compartment, 35: lower compartment, 39: Movable wall, 41: Fuel pump / piston, 43: Diaphragm, 45: Fuel pump chamber, 47: Ventilation chamber, 49: Port, 51: Fuel inlet part, 53: Pipe line, 55: Fuel supply source, 57: Non-return Valve device, 61: Fuel outlet part, 63: Pipe line, 65: Vaporizer, 67: Crankcase, 71: Check valve device, 75: Accumulator, 77: Cylinder, 79: Port, 81: Piston, 83: Spring , 91: oil pon Plunger, 93: Oil pump chamber, 95: Seal device, 101: Inlet part, 103: Pipe line, 105: Oil supply source, 107: Check valve device, 111: Outlet part, 113: Inner hole, 115: Branch port, 117: expanded central part, 119: check valve device, 121: movable wall, 123: low pressure chamber, 125: high pressure chamber, 127: motor / piston, 129: diaphragm, 131: central part, 135: Valve cage, 139: Seal, 141: Bias spring, 161: Pipe line device, 163: Main pipe line, 165: Low pressure branch pipe line, 167: High pressure branch pipe line, 169: Check valve, 171: Check valve 175: Bypass line, 177: Check valve, 177: Pressure release valve, 179: Pole member, 181: Seal, 183: Spring, 191: Central part port, 193: Valve member, 195 : Stem, 197: Axial center inner hole, 201: Valve member biasing spring, 211: Intermediate chamber, 213.215: Ring, 221: Column, 231: Sub chamber, 233: Floating piston, 235: Seal, 239: Cam, 241: Link device, 243: Throttle.

Claims (5)

[Claims] 1. At least one crankcase (67)
And a at least one pressure actuated motor (13), wherein the crankcase (67) alternately generates a high pressure and a low pressure having a frequency that changes with engine rotation, The pressure actuated motor (13) comprises a housing (15)
A movable wall (121) and a device (140) for reciprocating the movable wall (121), the movable wall (121) being arranged in the housing, the housing being arranged relative to each other. And a high pressure chamber (125) whose volume changes in the opposite direction, and the device (140) has a stroke with a frequency lower than the frequency of the pressure cycle of the crankcase. ,
Reciprocating the movable wall, the device (140) comprises means (151) for connecting the low pressure chamber and the high pressure chamber to one crankcase, whereby the low pressure chamber and A pressure difference is generated between the high pressure chambers, and by this pressure difference, the movable wall is movable in a direction that maximizes the volume of the high pressure chamber, and the connecting means (151) A first check valve (1) for allowing pressure to flow from the crankcase into the high pressure chamber.
71) and a second check valve (169) that allows pressure to flow from the low pressure chamber to the crankcase, and the device (140) has a volume of the high pressure chamber. A first spring (14) that biases the movable wall in a direction that minimizes
1) and a port (191) formed in the movable wall,
A valve member (193) that is movable between an open position and a closed position with respect to the port, the valve member being closed by a pressure difference between the low pressure chamber and the high pressure chamber. The movable wall is held in a position, and when the valve member is in the closed position, the movable wall is moved in a direction in which the volume of the high pressure chamber is maximized due to the pressure difference. The device (140) has a direction in which the valve member is opened and the movable wall minimizes the volume of the high pressure chamber when the movable wall approaches a position where the volume of the high pressure chamber is maximized. Means for holding the valve member in the open position during movement to a second spring (201) for engaging the valve member and opening the valve member in the open position. ) Has an internal combustion engine. 2. The internal combustion engine according to claim 1, wherein the means for opening the valve member and holding it in the open position comprises a member (302) engageable with the valve member, When the movable wall approaches the position where the volume of the high pressure chamber is maximized, the opening of the valve member is assisted by the engagement of the member (302) with the valve member. Internal combustion engine. 3. The internal combustion engine according to claim 1, wherein the means for opening the valve member and holding it in the open position comprises an intermediate chamber (211) provided in the low pressure chamber. The internal chamber communicates with the port to reduce a pressure difference between the high pressure chamber and the intermediate chamber. 4. The internal combustion engine according to claim 1, further comprising a fuel pump and an oil pump, the fuel pump including a fuel pump chamber and a fuel pump / piston. The fuel pump / piston is capable of reciprocating motion in the fuel pump chamber, and produces a flow of fuel in response to the reciprocating motion of the fuel pump / piston in the fuel pump chamber. A piston is movably coupled to the movable wall, the oil pump comprises an oil pump chamber, an oil pump piston, and a device for coupling the oil pump piston to the movable wall. The oil pump / piston is reciprocally movable in the oil pump chamber, and the oil pump / piston of the oil pump piston in the oil pump chamber is provided. The flow of oil is generated in response to the backward movement, the coupling device can stop the pumping operation of the oil when the pressure difference is smaller than a certain magnitude, and the pressure difference greater than the certain magnitude. An internal combustion engine, wherein the oil pump / piston is capable of reciprocating movement so that the oil supply amount can be increased with an increase in the size of the oil. 5. The internal combustion engine according to claim 4, wherein the coupling device that reciprocates the oil pump / piston reciprocates the movable wall in a part of the reciprocal motion of the movable wall. And is operable to cause a motion of the oil pump / piston, and is operable to cause a lost motion between the movable wall and the oil pump / piston in another portion of the reciprocating motion of the movable wall. Internal combustion engine characterized in that.