JPH06101646A - Cylinder head for air compressor - Google Patents

Abstract

PURPOSE: To accumulate and dampen the amplitude of pressure spikes of the compressed air discharged periodically through a discharge valve of an air compressor by forming an expansion chamber of a predetermined dimension on a body provided with a housing for communicating with a valve means. CONSTITUTION: An air compressor has a piston 70 engaged in a bore of a cylinder 62. The stroke of the piston 70 is set such that a flat end face 122 is tightly contacted with a reed plate 124 arranged between an end face of the cylinder 62 and a cylinder head 126. An outlet opening 128 communicating with an outlet chamber 130 which is an expansion chamber of the cylinder head 126 is formed in the reed plate 124. A reed valve 132 can be secured in a threaded opening 136 of the reed plate 124 by a bolt 134 via a central hole A reed stop member 138 is arranged for limiting the movement of the reed valve 132. The member is inclined to the direction departing from the reed plate 124.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates generally to an air compressor cylinder head, and more particularly to a relatively high output pressure, low capacity air compressor cylinder head particularly suitable for use in a fuel injection system for an internal combustion engine. The present invention is particularly preferably used in connection with each of the patent applications “air compressor” and “air compressor bracket” filed by the applicant on the same date as the present application.

[0002]

BACKGROUND OF THE INVENTION Over the years, many different types of air compressors have been developed over the years, depending on the particular intended use and application, with design considerations for each particular application. The history of the development of various air compressors is not explained here, but the recent developments in fuel injection systems for internal combustion engines are compact,
It has created a need for air compressors that operate reliably at high pressures and low capacities over a wide range of operating speeds. Such an air compressor is used for outboard motors,
It is particularly useful in fuel injection systems such as those used in two-stroke engines where the engine produces relatively large horsepower even though the engine is relatively small in size. Since the engine itself is of a relatively small size, the air compressor driven by the engine also occupies a relatively small capacity, while at the same time producing high pressure during crank operation at starting and at each operating speed in the range from idling speed to maximum speed Must occur.

The low capacity available in the air compressor raises the question of how to provide a sufficient amount of compressed air available by the engine. Also, because the air compressor must supply compressed air at the desired pressure level almost immediately to start the engine, the volume of compressed air in the outlet chamber does not require excessive cranking of the engine before starting. Can not be so big.

Accordingly, a primary object of the present invention is to provide an air compressor cylinder head configured to accumulate and attenuate the amplitude of pressure spikes in compressed air that is periodically discharged through an air compressor exhaust valve. It is in.

Another object of the present invention is to provide a cylinder head for an air compressor having a pressure damping conduit for delivering compressed air to a compressed air consuming device such as an internal combustion engine.

Yet another object of the present invention is to provide a total volume sufficient to dampen the amplitude of the compressed air pressure spikes to provide a sufficient amount of air, but which is necessary to start the engine. Another object of the present invention is to provide a cylinder head for an air compressor in which the desired minimum pressure level is not so great that it cannot be generated in a fairly short cranking period at engine start.

Objects and advantages other than those described above will become apparent from the following detailed description with reference to the accompanying drawings.

[0008]

SUMMARY OF THE INVENTION Broadly speaking, the present invention is capable of providing a relatively high output pressure with a relatively low capacity, and is also useful in an internal combustion engine such as an outboard engine. It concerns a compact design air compressor capable of operating over a wide range of speeds as occurs when the compressor is driven. The air compressor is driven by an external power source such as an outboard engine via a drive belt that drives a drive pulley.

The drive pulley is connected to the crankshaft structure, and the crankshaft structure is connected to the reciprocating piston via a connecting rod. The piston reciprocates inside a cylinder bore having a side inlet for introducing air, and the piston compresses the air, forcing the air into the outlet chamber communicating with the air pressure regulator via the reed valve mechanism. Delivered to provide a constant desired output pressure.

The air compressor of the present invention preferably provides an output pressure of about 80 pounds per square inch, but can produce output pressures well above that value depending on operating speed. In one possible specific application, an air compressor is used to supply air to a fuel injection system for an internal combustion engine, such as an outboard engine.
The air compressor cooperates with an air pressure regulator used to maintain a nearly constant pressure supply used in the fuel injection system. Since the desired output pressure is about 80 pounds per square inch, the present invention operates at a slightly higher pressure, 90 psi, with the air compressor crankshaft operating at about 610 revolutions per minute (rpm). About every minute 1.
Given in a capacity of 6 cubic feet (CFM). A typical idling speed of an outboard engine to which an air compressor can be attached is 550 to 650 rpm. Therefore,
The lower idling speed of the engine is 550 rp
The air compressor and motor pulleys must be sized so that the air compressor operates at about 610 rpm even at m. Engine is generally about 6000 rpm
Even when operating at maximum speed, the output pressure is maintained at 80p.si by the air pressure regulator connected to the outlet chamber, but the air volume generated at such speed is about 7 cubic meters per minute. It's feet.

The speed versus power characteristic is shown in FIG.
It shows that the characteristic is almost linear until the operating speed increases in the upper part of the range. However, in the upper range, the efficiency of the air compressor generally decreases and the output does not increase linearly with increasing speed. This is because during the reciprocating movement of the piston, the period during which the inlet opens gradually becomes shorter and air cannot pass through the inlet to fill the cylinder bore. In the application of supplying compressed air to the fuel injection system for the outboard engine, the air capacity required for the fuel injection system is only about 6 CFM, and the air capacity generated above this value is simply released. Since it is not used, the above efficiency reduction is rather advantageous. By not producing a large volume well beyond what is needed, the escape is minimized and less work is needed to compress the air, resulting in increased effective power output of the engine.

As will be described later, the air compressor is driven by a drive belt that spans from a pulley attached to the crankshaft of the engine to a drive pulley of the air compressor. By changing the size of one or the other of the two pulleys that the drive belt runs around,
It is easily understood that the operating speed of the air compressor can be adjusted with respect to the speed of the engine.

Also, as will be explained later, the air compressor is capable of operating over a very wide range of operating speeds, so that considerable heat is generated during operation. For this reason, the air compressor has an oil system that lubricates the air compressor itself, and the cylinder region is water-cooled to effectively dissipate the generated heat.

[0014]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT Referring now to the accompanying drawings, and in particular to FIG. 1, an air compressor, generally designated 20, is shown in connection with an outboard engine having an engine block 22. The engine block 22 is a part of a V6 type engine having left and right head surfaces 24 and 26 schematically shown, and has a rear portion 28. The center line of the engine crankshaft is 30
It is indicated by. The engine block 22 also has an upper opening 32 therein for containing cooling water, and the air compressor 20 is configured to be mounted on top of the engine block 22 and has a generally flat lower surface. It has the mounting bracket portion 34 shown, and the mounting bracket portion 34 covers the opening 32 of the engine block 22 and bolts to the engine block 22 by bolts (not shown) inserted through the six openings 36. Will be stopped.

A hole 38 is formed in the center of the mounting bracket portion 34, and a pressure relief valve, generally designated by 40, is bolted to each boss by two bolts 42 inserted into the threaded holes to provide pressure relief. A pair of nipples 4 of the valve 40
Hose can be attached to each of 4 and engine block 2
Pass water from inside the 2 into the engine cylinder. The pressure relief valve 40 is shown to be located in a position where it will perform its normal function and is not part of the invention itself and is part of the engine, and is found on many outboard engines. .

When the air compressor of the present invention is used for a purpose different from that shown in the drawing, the boss and the mounting bracket portion 3 are used.
It will be readily understood that the four holes 38 and 42 need not be provided. Also, for applications other than those shown, the entire mounting bracket portion 34 may have a different shape or may be substantially removed. Furthermore, the mounting bracket part 34 has an outer extension 46, the upper surface 48 of which lies in a plane higher than the general plane of the mounting bracket part 34, this plane change being compensated for by the connection at the ramp 50. There is. The outer extending portion 46 is provided for fixing the idler pulley 52 (see FIG. 13).

The air compressor 20 is driven via a drive belt 58 (FIG. 2) by a pulley 54 mounted on the crankshaft of the engine, which drive belt 58 is partially shown in FIG. The drive belt 58 is wound around the drive pulley 56 that is most clearly shown in FIG. 2, and the back side of the drive belt 58 is in contact with the idler pulley 52. As will be described later, the idler pulley 52 can be adjusted so that the tension of the drive belt 58 can be changed.

According to the present invention, the mounting bracket portion 34
Is preferably cast in one piece with the crankcase 60 and the cylinder casting 62 and is provided with reinforcing ribs 64, 66 and 68 to strengthen the entire casting.

As shown most clearly in FIGS. 1 and 2, the air compressor 20 includes a piston 70 that fits within the cylindrical bore of a cylinder casting 62 (cylinder bore).
And the bore is preferably formed by a separate cylindrical sleeve 72 which is preferably cast into place during casting of the cylinder casting 62, crankcase 60 and mounting bracket portion 34. Piston 70 has slots near its head portion that receive three rings 74, 76 and 78, respectively, of which ring 78
The piston 70 and the sleeve 7 are in operation during operation as will be described later.
It is an oil ring that works to pass the oil existing between the two surfaces.

The piston 70 is connected to a connecting rod 80 by a wrist pin 82, while the other end of the connecting rod 80 is connected to a pair of crankshaft members 84 by a crankpin 86 fitted in a needle bearing assembly 88. Is
The outer surface of the needle bearing assembly 88 fits within the opening of the connecting rod 80. The crank pin 86 is press-fitted into each hole of the crank shaft member 84 to fix and maintain both members at a predetermined position relative to each other. The crank shaft member 84 is
Each has an integral cylindrical extending portion 90, 92, the outer surfaces of these cylindrical extending portions 90, 92 are rotatably supported in each bearing 94, and one cylindrical extending portion 90 is a drive pulley. A small diameter threaded extension 96 that receives 56 and is fixed by a nut 98 from relative rotation.
Have That is, as shown in the drawing, the drive pulley 56 is
Having a radially extending shoulder 100 that abuts the end of the cylindrical extension 90, a nut 98 allows the drive pulley 56 to be clamped and secured to the cylindrical extension 90. An annular seal member 102 is provided to prevent oil from escaping from the crankcase 60. As the annular seal member 102, for example, a lip seal manufactured by Chicago Rawhide of Chicago, Illinois, USA can be used. The connecting rod 80 has a hole through which the wrist pin 82 passes, and between the wrist pin 82 and the opening of the connecting rod 80, a needle bearing assembly 1 different from the one described above is provided.
04 is provided to allow rotation of the connecting rod 80 relative to the cylinder during operation.

Since the cylindrical extension 92 extends beyond the opening, it can be utilized to extract power for powering another component, such as a power steering pump, if desired.
This point can be achieved by attaching the jack shaft 95 or the like to the cylindrical extension portion 92 of the crankshaft member 84 via the threaded opening 93.

The crankshaft member 84 must be inserted into the inside of the crankcase 60, and the integral cast body consisting of the mounting bracket portion 34, the cylinder cast body 62 and a part of the crankcase 60 is a single cast body. It should be understood that it is a structure. Therefore, the crankcase 60 has a divided structure, and the end cast body 104 can be removed from the crankcase 60 along the dividing line 106. The end casting 104 is shown in FIGS.
In detail. For example, FIG. 9 showing an internal view of the end cast body 104 when viewed along the dividing line 106 in FIG.
2, the end casting 104 includes a pair of annular grooves 1 that each receive a C-shaped retaining ring 110 (FIG. 2).
08, each retaining ring 110 is in contact with the outside of the ball bearing assembly 94. Then, the seal member 102
Respectively contact the other side of the retaining ring 110. In addition, the groove 108 is also provided in the crankcase cast body 60, and C
The V-shaped retaining ring 110 may provide a substantially continuous annular groove into which it can fit. C-shaped retaining ring 1
10 is preferably used, but a flat washer may be used instead. The use of the retaining ring 110 provides a simple, inexpensive but effective means for accurately positioning the crankshaft member 84 within the crankcase 60 and allowing easy assembly and disassembly. As shown in FIGS. 7 and 9, the end casting 10
4 are attached to the crankcase 60 by four bolts (not shown) inserted into the openings 112, respectively.

From the above description of the structure of the crankcase assembly and piston 70, connecting rod 80 and related parts, the drive pulley 56 connected to the motor or other power source is driven by the drive belt 58, and the crank It should be understood that the shaft is rotated causing the piston 70 to reciprocate within the cylinder bore formed by the cylindrical sleeve 72.

Cylindrical sleeve 72 and cylinder casting 62 have multiple openings 114 that introduce air into the cylinder bore at two different times during operation of air compressor 20. One time is when the air is compressed for main output, which is when the piston 70 is at its bottom dead center,
That is, it occurs when it is on the right side of the position shown in both FIG. 1 and FIG. The other time occurs when it is in the position shown in both FIGS. 1 and 2 which introduces air into the cylinder, after which the piston 70 moves to the right from top dead center to bottom dead center, Air is crankcase 6
Compressed inside 0, providing a low pressure level but auxiliary output.

The above-described ability to introduce air at the two positions of the piston 70 is such that each inlet opening 114 has a piston 7
Located approximately midway along the zero stroke, the side wall length of the piston 70 results from the configuration being less than half the stroke length of the piston 70.

The inlet openings 114 are also shown in phantom in FIG. 1 and consist of five openings, each preferably about 3/8 inch in diameter. In FIG. 1, these inlet openings 114 are actually located above the connecting rod 80, in the portion of the cylinder wall 62 that is removed in the figure. The position of the inlet opening 114 with respect to the end of the piston 70 at bottom dead center is about 0.075 from the opening edge from the leftmost side in FIG.
Inches are preferred. This results in an effective aperture consisting of a portion of the circular aperture and measuring about 0.075 inches by about 0.400 inches.

The position of the inlet opening 114 with respect to the head end of the cylinder bore, that is, the left end in FIG. 1, affects the output characteristics shown in FIG. The farther the inlet opening 114 is located from the head end, the greater the effective stroke of the piston 70 and the more efficient the air compressor 20 is at low operating speeds. On the contrary, if the inlet opening 114 is located closer to the head end, the time during which the inlet opening 114 is not covered during the reciprocating movement of the piston 70 becomes longer, and more air is introduced into the cylinder bore. Becomes more efficient at high operating speeds.

An intake manifold 116 is provided in the region of the inlet opening 114 and is attached to the cylinder casting 62 with a plurality of bolts (not shown) and also the intake manifold 116.
A gasket 118 is preferably placed at the boundary between the cylinder casting 62 and the cylinder casting. The intake manifold 116 includes an intake opening 12 for introducing air into the manifold 116.
Has 0. Inside the intake manifold 116, it is preferable to provide filter means (not shown) for preventing dust and debris from entering the cylinder. As shown most clearly in FIG. 2, the piston 70 has a flat end surface 122 such that the end surface 122 closely contacts a lead plate 124 disposed between the end surface of the cylinder 62 and the cylinder head 126. The stroke of the piston 70 is preferably fixed. The lead plate 124 has an outlet opening 128 that communicates the cylinder bore with an outlet chamber 130 that is an expansion chamber of the cylinder head 126.
Preferably there are eight. The lead plate 124 must be thick enough so that it will not deform under exposed temperature and pressure levels, while the piston 70 moves during movement.
It should be as thin as possible to allow for greater air compression. That is, with a thin structure, the volume between the bottom of the reed valve 132 and the top of the piston 70 at the top dead center is reduced, and a larger compression ratio is provided accordingly.

As shown in FIG. 18, a reed valve 132 having a shape having eight petal (petaloid valve plate) structures is provided, and the reed valve 132 has a center hole, and the center hole is used to insert the center hole. The bolt 134 can be tightened in the threaded opening 136 of the lead plate 124. Further, a reed stopper member 138 for restricting the movement of each petal of the reed valve 132 is provided, and its shape is substantially the same as that of the reed valve 132, but its size is somewhat smaller than that.

As shown in FIG. 2, the lead stopper member 1
Since the respective petals 38 are inclined in the direction away from the reed plate 124, the respective petals of the reed valve 132 are bent in response to the pressure generated by the action of the piston 70 in the stroke toward the left side in the drawing, and the compressed air is discharged. While communicating with the inside of the chamber 130, when the piston 70 moves to the right side, each petal of the reed valve 132 returns to the position shown and closes the valve, so that the pressure in the outlet chamber 130 is increased by the piston 7.
Even if 0 moves to the right, it does not decrease.

According to an important feature of the invention, the reed valve 1
32 is preferably made of stainless steel flap valve material, which preferably has a thickness of 0.011 inches, and the shape of each outlet opening 128 is the same as the shape of the individual petals, but the valve The petal is slightly larger than the outlet opening 128 so that the petal will not be sucked into the outlet opening 128 when closed. That is, there is overlap between each petal and both outer edges of the outlet opening 128 so that the reed plate 124 provides a contact surface for stopping the petal of the reed valve 132,
This overlap is preferably about 0.060 inches at the pressure level produced by the present invention. Reed valve 13
In the second petal, the internal pressure of the cylinder bore is equal to that of the outlet chamber 130.
It operates when the internal pressure is exceeded. The lead petal construction described above provides sufficient deflection to open the valve with a differential pressure of about 5 pounds per square inch. The lead petal construction described above also provides sufficient rigidity to withstand the differential pressure of the outlet chamber 130 with respect to the cylinder bore, which can reach up to about 90 pounds per square inch as the piston 70 moves to the right. .

As described above, the reed stopper member 138 is provided to limit the movement of the reed valve 132 during operation. The shape of the reed stopper member 138 is the reed valve 13
2 is substantially the same as itself (see FIG. 18), but the size is somewhat smaller as shown in FIGS.
The reed stopper member 138 is made of a metal having sufficient rigidity to stop the reed valve 132 from bending. Further, the reed stopper member 138 is inclined in a direction away from the reed plate 124 as shown in FIGS. 1 and 2, and enables the reed valve 132 to be flexed in a limited manner. Lead plate 12
4 for sealing between the cylinder 4 and the cylinder wall 62
40 is provided, and another gasket 142 is provided between the lead plate 124 and the cylinder head 126. Each gasket 140, 142 extends along the outer periphery of the lead plate 124, but has a number of openings 144 for communicating during operation, as will be described later.

Referring to FIGS. 1, 3, 4, 5, and 16, the cylinder head 126 is connected to a conduit 148 in relation to the outlet chamber 130 and has an extension generally indicated at 146. A conduit 148 has an increased volume with respect to the outlet chamber 130 and acts as an accumulator. Extension 146
Has a port 150 communicating the outlet chamber 130 with a lateral opening 152, in which a conduit 148 is connected. As shown most clearly in FIG. 3, conduit 148
Is an outer annular fitting 154 for attachment to the opening 152.
And an O-ring seal 156 is provided to prevent air from leaking out of the conduit 148 and the interior of the outlet chamber 130. Seal 156 is preferably made of Viton or other material that can withstand operating temperatures up to 600 ° F. The cylinder head 126 is attached to the cylinder casting body 62 by bolts (not shown) inserted into the openings 166 at the four corners.

As shown in FIG. 16, the conduit 148 is connected to a pneumatic regulator 158 of conventional construction, which in the preferred embodiment is the pneumatic regulator 15.
8 limits the air pressure in conduit 148 to the desired level, which is about 80 psi. An outlet line 160 from the air pressure regulator 158 is provided to direct the desired air pressure to the left and right fuel / air rails 163 and 165, which fuel / air rails 163, 165 are part of the engine fuel injection system. Thus, they themselves do not form part of the invention.

The volume of conduit 148 and outlet chamber 130 preferably totals about 200 cubic centimeters (CC). That is, the outlet chamber 130 preferably has a volume of about 50 cubic centimeters and the conduit 148 is
It preferably has a volume of about 150 cubic centimeters. Conduit 148 is connected as shown in FIG.
It is about a foot long and extends over substantially the entire length of the engine block 22. As shown in FIG. 1, the conduit 148
Has two corners so that it can be located in its immediate vicinity as it extends along the entire length of the engine block 22. It should be noted that the length of the conduit 148 and its inner diameter necessarily affect the pipe volume, and in the particular application of the air compressor 20 illustrated in connection with an internal combustion engine, the outlet chamber 130 and the conduit 1
It should be appreciated that the total volume with 48 is preferably about 200 cubic centimeters.

The size of the outlet chamber 130 and the conduit 148 should be large enough to act to damp the high pressure spikes created by the operation of the air compressor 20, while filling takes too long and starts the engine. It must not be so large that the engine must crank too much before sufficient pressure is generated. In a preferred embodiment intended for use in a 3 liter V6 type internal combustion engine, it is preferably rigid to withstand the heat generated during operation of air compressor 20, but is made of a material that will not be damaged by heat. If so, it may be flexible. If it is flexible, the damping effect is further improved.

It should be noted that although the outlet chamber 130 can be larger than the illustrated example, the physical size of the air compressor 20 in the illustrated preferred embodiment is such that the cylinder head 126 is defined in FIGS. 1 and 2. It indicates a limit that should not extend beyond existing boundaries.

As described above, the air compressor 20 is
It also provides an auxiliary pressure output generated by the compression of air in the crankcase 60 during the stroke of the piston 70 in the reverse direction, that is, to the right. This is because when the piston 70 moves the stroke to the top dead center and moves to the return stroke, air is introduced into the inside of the cylinder bore through the inlet opening 114, and then the piston 70 moves to the right side,
It is caused by sealing the inlet opening 114 by the side wall of the piston 70 itself and further compressing the air in the crankcase 60 with the movement of the piston 70 towards bottom dead center.

The level of pressurization is much lower than the pressure applied in the outlet chamber 130, which is about 10 p.si, and the output of the auxiliary pressure from the crankcase 60 is at such a low pressure level. It is controlled by the air check valve 168 shown in FIGS. 1, 7 and 10. Air check valve 168
Preferably has an integrally formed nipple 170, and a pipe such as 172 can be attached to the nipple 170 to provide auxiliary pressure to an accessory such as a low pressure fuel discharge pump or an oil metering pump. Air check valve 168
Is preferably in communication with the inside of the crankcase 60 via the port 174 and opens and closes with a very small differential pressure in any direction across the check valve 168.

To lubricate the piston 70 and the bearings in the crankcase 60, the air compressor 20 includes an oil supply line 176 (FIG. 1) connected together to an oil distribution pump.
6)) and an oil drain line 178. Referring to FIG. 7, the refueling line 176 is attached to the refueling check valve 180,
Is connected to the end casting 104 and communicates with the crankcase 60 via a port 182. Oil drain line 178
Is a drain fitting 18 with an orifice as shown in FIG.
4 and the drain fitting 184 is connected to the crankcase 60 via the port 186 shown in FIGS. 7, 8 and 9.
Is in communication with.

The position of the refueling check valve 180 is at the top of the crankcase 60, while the drain attachment device 184 with an orifice for returning oil is located at the bottom of the crankcase 60 and circulates oil in the crankcase 60. It is understood that the effect of gravity is utilized in the crankcase 60, and that the crankcase 60 is not filled with oil, but sufficient oil flows through the crankcase 60 to maintain proper lubrication. Should be. Further, the air check valve 168, which is the source of the auxiliary pressure, is arranged near the top of the crankcase 60.

According to an important feature of the present invention, the refueling check valve 180 and the drain fitting 184 are used because the crankcase 60 itself is used to generate the auxiliary air pressure. That is, rather than pumping through the crankcase 60, the pressure level within the crankcase 60 provides a negative pressure to draw oil into the crankcase 60 through the inlet. The pressure level in crankcase 60 is approximately 4 psi for the oil in refueling line 176.
Produces a negative value of. The refueling check valve 180 is configured so that the pressure in the refueling line 176 reduces the pressure in the crankcase 60 by about 10 times.
Open only when psi is exceeded. Therefore, at the time of operation, when the differential pressure exceeds the above value, the refueling check valve 180 opens to allow the oil to be sucked into the crankcase 60,
During other operations, the oil is not sucked into the crankcase 60.

The oil pressure normally applied to refueling line 176 is a minimum of about 10 psi. The oil drain fitting 184 is large enough to drain all the oil that has flowed into the crankcase 60, while it also provides an auxiliary pressure source for accumulating pressure in the crankcase 60 to operate the other accessories described above. It has an orifice that is small enough not to interfere with delivery. From this point, the diameter is about 0.03
It has been found that a 0 inch orifice is sufficient to achieve adequate pressure levels while at the same time draining the oil from the crankcase 60 at the desired flow rate.

9 and 10 to help oil flow from the inlet port 182 to the outlet port 186 and in view of the outer diameter of the crankshaft member 84 being close to the opening size of the end casting 104. As shown, an oil groove 188 is provided inside the crankcase 60.

The oil also moves to the piston 70,
Lubricate the piston 70 in the sleeve 72. For the reasons mentioned above, it is important to minimize the amount of oil contained in the air at output pressure, so that three rings 74, 76 and 78 are provided, 78 of which are oil rings. As shown in FIG. 17, the oil ring 78 includes a wavy portion 192 between upper and lower thin ring portions 190.
It has a composite structure formed by sandwiching. This wavy structure allows oil to pass through the ring 78 during operation, and the oil that has passed through the piston 7 through the six openings 194 present in the piston 70 as shown in FIGS. 1 and 15.
It is possible to move inside 0. That is, as shown in FIG. 15, when recesses are formed by casting at six places as viewed in the axial direction of the piston 70 and a groove for the ring 78 is cut, an opening is cut at a corresponding position on the piston 70 side. Oil can pass into the piston 70 through the openings 194 at the respective positions.

Since heat is generated by the air compressor 20, a cooling system is provided for the region of the cylinder head 126, and for this purpose the cylinder casting 62 is
There is a space 196 that extends almost all around, and a space 198 (see FIG. 6) is formed in the cylinder head 126 as well. As described above, the air compressor 20 has the mounting bracket portion 34 that fits into the opening of the engine block 22 that contains the cooling water inside, and the water from that area is supplied to the internal port 200 (see FIGS. 1 and 2). 12) to each space 196, 198, and the port 200 extends from the opening of the engine block 22 to the space 196. The water flows through the space 196, the opening 144 of the lead plate 124, and both gaskets 140, 1.
It circulates through 42 equally sized openings. The water is then withdrawn through an opening 202 which receives an outlet fitting 204, which has a nipple to which a pipe can be attached to expel the water at a convenient location. Outlet fitting 2
04 controls approximately 40 psi to control the flow rate of cooling water.
When used in an outboard motor having a water pressure of about 1/4 inch, it has an orifice of about 1/4 inch.

It is important that the temperature of the compressed air be controlled within a certain range. When the temperature exceeds the carbonization temperature of the lubricating oil used in the air compressor 20, the piston 70
There is a risk that carbon will adhere to the top part of the fuel cell, will be peeled off in the form of flakes and will be mixed in the compressed air, and will adversely affect the operation of the fuel injection system. Also, if the temperature becomes too low to cause water condensation, water mixes with the oil that may be present in the output compressed air, forming a sludge-like mixture,
Similarly, the operation of the fuel injection system may be adversely affected.

Referring to the idler pulley 52 shown in FIG. 13, the idler pulley 52 is mounted so as to be adjustable in order to adjust the tension of the drive belt 58. With reference to FIGS. 1, 12, 13 and 14, the outer extending portion 46 of the mounting bracket portion 34 has a crescent-shaped opening 206, and the mounting bracket 208 of the hexagonal head is provided with a small bolt 210. It is attached to the extension. If a wrench is applied to the mounting bracket 208 of the hexagonal head, the bracket 208 can be rotated around the bolt 210 to obtain a desired tension on the drive belt 58, and the bolt 2 with the nut 214 after adjustment can be obtained.
12 can be tightened and maintained in the desired position. The mounting bracket 208 is shown in one position in solid lines in FIG. 1 and in another position in phantom lines. The idler pulley 52 includes an internal bearing 216.

The embodiments of the present invention have been shown and described above.
It should be understood that various other alternatives, substitutes and equivalents can be used, and the present invention is limited only by the description of the claims and their equivalents.

Various features of the invention are set forth in the appended claims.

[0051]

As described above, according to the cylinder head for an air compressor of the present invention, it is possible to accumulate and attenuate the amplitude of the pressure spike of the compressed air periodically discharged through the exhaust valve of the air compressor. it can.

[Brief description of drawings]

FIG. 1 is a plan view with a portion of an air compressor embodying the present invention removed, shown in the environment of an outboard engine.

2 is a partial cross-sectional front view of the air compressor shown in FIG. 1, with a part removed.

3 is a left end view of the air compressor shown in FIG.
Especially, it shows a cylinder head.

FIG. 4 is a sectional view taken substantially along the line 4-4 in FIG.

5 is a front view of the cylinder header of FIG.

6 is a bottom view of the cylinder header of FIG.

FIG. 7 is a right side view of a part of the air compressor shown in FIG.

8 is a side view of the structure shown in FIG.

9 is a right side view of the structure shown in FIG.

FIG. 10 is a sectional view taken substantially along the line 10-10 of FIG.

11 is another cross-sectional view substantially taken along the line 11-11 of FIG.

12 is a sectional view taken substantially along the line 12-12 in FIG.

13 is a side view taken substantially along the line 13-13 in FIG.

FIG. 14 is a side view taken substantially along the line 14-14 of FIG.

FIG. 15 is an end view of a piston used in the air compressor of the present invention.

FIG. 16 is a simplified diagram of an air compressor embodying the present invention, showing an output pipe, and also showing a part of a fuel injection system for an outboard engine and an air pressure regulator.

FIG. 17 is a side view of a part of the oil ring structure used in the piston of the present invention.

FIG. 18 is a plan view of a reed valve used in the present invention.

FIG. 19 is a graph showing the relationship between operating speed and output capacity of an air compressor embodying the present invention.

[Explanation of symbols]

 20 Air Compressor 60 Crankcase 62 Cylinder Cast Body 70 Piston 124 Reed Plate 126 Cylinder Head 130 Outlet Chamber 132 Reed Valve 148 Conduit

Front Page Continuation (72) Inventors Robert Elle, Neem Tick, Illinois, USA 60046, Lakeville, Nathan Hale Drive South 36453 (72) Inventors Harold, K, Wade, Illinois, USA 60087, Wookeygan, Chaplin 13577

Claims (11)

[Claims] 1. A pressure spike of compressed air, comprising a housing, at least one cylinder located within said housing, reciprocating within said cylinder to periodically compress a quantity of air. In a cylinder head for an air compressor having a piston for periodically discharging the air through a valve means, a main body provided in the housing so as to communicate with the valve means, and a main body formed in the main body for holding a predetermined amount of compressed air An expansion chamber sized to accumulate and dampen the amplitude of pressure spikes of compressed air exhausted through the valve means until. 2. The cylinder head for an air compressor according to claim 1, wherein the expansion chamber has a compressed air storage capacity of about 50 cc. 3. An expansion conduit in fluid communication with the expansion chamber, the expansion conduit having an additional storage capacity and configured to deliver compressed air to a compressed air consuming means. The cylinder head for an air compressor according to claim 1. 4. The cylinder head for an air compressor according to claim 3, wherein the expansion conduit has a compressed air storage capacity of about 150 cc. 5. The cylinder head for an air compressor according to claim 3, wherein the expansion conduit chamber is rigid. 6. The cylinder head for an air compressor according to claim 3, wherein the expansion conduit chamber is flexible. 7. The cylinder head for an air compressor according to claim 3, wherein the compressed air consuming means is an internal combustion engine. 8. A cylinder head for an air compressor, comprising a piston that reciprocates in a cylinder and discharges a pressure spike of compressed air to an internal combustion engine through a valve means, the cylinder head being provided in a housing so as to communicate with the valve means. And a pressure spike formed in the body for accumulating the amplitude of pressure spikes of compressed air exhausted through the valve means until a predetermined amount of compressed air is held for transmission to the internal combustion engine at a constant pressure. A cylinder head for an air compressor, comprising an expansion chamber dimensioned to dampen. 9. The cylinder head for an air compressor according to claim 8, wherein the expansion chamber has a compressed air storage capacity of about 50 cc. 10. An expansion conduit in fluid communication with the expansion chamber, the expansion conduit having an additional storage capacity and configured to deliver compressed air to the internal combustion engine. The cylinder head for an air compressor according to claim 8. 11. The cylinder head for an air compressor according to claim 10, wherein the expansion conduit has a compressed air storage capacity of about 150 cc.