Swing type air compressor

Abstract

To solve the problem of compression heat caused by the presence of a bearing in a piston, and to widen the application range of an air compressor.SOLUTION: A rocking arm is rocked through a small end of a driving side connecting rod 15 connected to a crankshaft 16, the other end is connected to a connecting rod part bearing of a piston 13 integrated with the connecting rod in a housing 9, and rotary motion of the crank 16 is converted into rocking motion by a quadric link mechanism to reciprocate the piston 13 through a driven side connecting rod connected to the other end of the rocking arm.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to an oscillating air compressor. [Background technology]

[0002] In conventional crank-piston reciprocating air compressors, the small end bearing of the connecting rod is connected to the piston via the piston pin (see Figure 13).

[0003] This is because, even if the connecting rod and piston are directly connected as shown in Figure 14, the rotational motion of the crankshaft cannot be converted into the reciprocating motion of the piston. The connecting rod F in Figure 14 oscillates at an angle α (Figure 14) symmetrical to P. The connecting rod itself rotates at its big end due to the rotational motion of the crankshaft, while its small end oscillates while performing a linear reciprocating motion to reciprocate the piston. Therefore, the piston side requires a bearing and pin (piston pin) to accommodate this oscillating motion. However, air compressors generate compression heat when compressing air. Air compressors, especially oil-free air compressors that require oil-free air on the discharge side, cannot use lubricating oil in the bearings, and therefore cannot be cooled by lubricating oil. For this reason, the pistons mentioned above use bearings pre-filled with grease, but the bearings can only withstand a maximum temperature of around 100°C, which limits the discharge pressure and air volume. Summary of the Invention [Problem to be solved by the invention]

[0004] The air compressor has a crank-piston structure where the piston moves back and forth in a straight line, and the cylinder is cooled by air. The bearing connecting the piston and the connecting rod is exposed to high temperatures because it is very close to the bearing and receives the heat of compression during compression. The temperature of the gas after the adiabatic change, T 2, and the temperature rise T of the gas due to adiabatic change 2-T1 is p1 = atmospheric pressure = 0.1013 MPa, p2 = (0.7 + 0.1013) MPa. T2-T1=T1{(p2 / p1) (κ-1) / κ -1} [°K]. When T1 = 30°C, T2 is calculated as T2 = T1 (30 + 273) × ((0.7 + 0.1013) / 0.1013) (1.4-1) / 1.4 =547.1 °K=274.1 T2-T1=274.1° T2 = 274.1 + 30 = 304.1°C. In an actual compressor, the temperature is lower than this because the heat dissipation fins on the cylinder are cooled by a cooling fan, but the temperature inside the compressor cylinder can reach a considerable level. [Means for solving the problem]

[0005] This invention solves and further develops the problems of conventional air compressors using a crank-piston movement mechanism, and its first structure comprises a crankshaft passing through a housing via a bearing, a drive-side connecting rod attached to the crank pin of the crankshaft via a large-end bearing, a drive-side pin attached to the drive-side connecting rod via a small-end bearing, and a swing arm having one end and the other end, one end of which is connected to the drive-side pin and the middle of which is passed through by a swing shaft passing through the housing, the swing arm having a drive-side swing arm portion and a driven-side swing arm portion; a piston integral with a driven connecting rod connected via a bearing to a driven pin provided at the other end of the swing arm, the piston having piston rings around its upper and lower ends, and slidably fitted in a cylinder of the compression unit without a piston pin; a cylinder having cooling fins formed around its periphery and integrally provided on an upper portion of the housing; a valve plate having an intake port with an intake valve and an outlet port with a discharge valve and integrally provided on the cylinder; and a valve cover having an intake port and an outlet port and integrally provided on the valve plate; An oscillating air compressor in which an oscillating arm is oscillated via the small end of a driving connecting rod connected to a crankshaft, and the other end is connected to a connecting rod portion bearing of a piston that is integral with the connecting rod within the housing, and the rotational motion of the crank is converted into oscillating motion by a four-bar linkage mechanism, causing the piston to move back and forth via the driven connecting rod connected to the other end of the oscillating arm.

[0006] The second structure of the oscillating air compressor described in claim 1, characterized in that the rotational movement of the crankshaft causes the other end of the oscillating arm or the driven oscillating arm portion to move in an approximately reciprocating linear motion in the direction of the reciprocating linear motion of the piston.

[0007] 2. The oscillating air compressor according to claim 1, wherein the third structure is characterized in that the driven-side oscillating arm portion is connected to the connecting rod of the piston at a substantially right angle or in a perpendicular state.

[0008] The fourth structure is the oscillating type air compressor according to claim 1, characterized in that the driven side oscillating arm portion is connected to the connecting rod so as to be perpendicular to the connecting rod of the piston when the piston is positioned in the middle of its reciprocating stroke.

[0009] The fifth structure includes a drive unit having a crankshaft passing through a drive unit housing via a bearing, a drive unit side connecting rod attached to a crank pin of the crankshaft via a large end bearing, a drive unit side pin attached to the drive unit side connecting rod via a small end bearing, a drive unit side swing arm connected to the drive unit side pin, and a swing shaft passing through the swing arm and into the housing; a first compression unit having cooling fins on the periphery and a cylinder with an opening at the center inside the middle part; a second compression unit having cooling fins around the periphery and a cylinder with an opening at the center inside a middle part, the second compression unit having a compression unit housing formed symmetrically with the first compression unit about the swing axis; a valve plate having an intake port with an intake valve and an exhaust port with a exhaust valve, the valve plate being integrally provided on a cylinder of the first compression unit; and a valve cover having an intake port and an exhaust port, the valve plate being integrally provided; a piston having piston rings around its upper and lower ends, respectively, and integrally provided with a connecting rod having no piston pin and slidably provided in a cylinder of the first compression unit; a first compression unit housing provided integrally with the swing shaft and having a driven swing arm portion connected at one end to both of the driven connecting rods; a piston having piston rings around its upper and lower ends, respectively, and integrally provided with connecting rods each having no piston pin and each slidably fitted in a cylinder of the second compression unit; a second compression unit housing having a swing shaft provided horizontally at the center between the two compression unit housings, and a driven-side swing arm portion provided integrally with the swing shaft, the other end of which is connected to both of the driven-side connecting rods; a connecting flange for concentrically connecting the centers of the swing shafts connecting the compression unit housing and the drive unit housing; The lower end of the piston integrally formed with the connecting rod in the first compression unit is connected to one end of the driven swing arm, and the lower end of the connecting rod of the piston integrally formed with the connecting rod in the second compression unit is connected to the other end of the driven swing arm. The rotational motion of the crank is converted into swing motion by a four-bar linkage to swing the driven swing arm, causing the piston to perform approximately linear reciprocating motion via the driven connecting rod connected to both ends of the driven swing arm. Both ends of the driven swing arm are caused to perform approximately linear reciprocating motion in the direction of the piston's reciprocating linear motion. The driven swing arm is connected to the connecting rod of the piston approximately perpendicular or perpendicular to it. Alternatively, the driven swing arm is connected so as to be perpendicular to the connecting rod when the piston is positioned midway through its reciprocating stroke.

[0010] In this invention, the connecting rod and piston are integrated, and the only bearing is at the end of the connecting rod opposite the piston, which makes it possible to eliminate the bearing on the piston side. This separates the connecting rod bearing from the compression heat, making it possible to almost completely eliminate the effects of compression heat. Furthermore, this structure allows the connecting rod and piston to move in an approximate linear reciprocating motion as a single unit. [Effects of the Invention]

[0011] By integrating the connecting rod and piston and using only the bearing on the end of the connecting rod opposite the piston, it is possible to eliminate the bearing on the piston side. This separates the connecting rod bearing from the heat of compression, making it possible to almost completely eliminate the effects of compression heat. In particular, oil-free air compressors, which do not use lubricating oil, use piston pins and needle bearings on the conventional pistons, and the bearings are filled with grease to lubricate them. Rubber seals are used to seal the grease, and the operating temperature limit for these grease and rubber seals is around 100°C.

[0012] In particular, in oil-free air compressors that require air that does not contain lubricating oil on the discharge side, if the cylinder cooling method is air-cooled and the discharge pressure is around 0.8 MPa and the motor capacity of one cylinder is 3 kW or more, the compressor discharge temperature will exceed the temperature mentioned above, and the bearing temperature of the piston pin will become the limit. In addition, temperatures close to the limit of use will inevitably have a negative impact on the life of the bearing.

[0013] In such cases, the air compressor of the present invention, which has a piston integrated with a connecting rod, can overcome the problems caused by the compression heat mentioned above, and can also solve the problems caused by providing a piston pin on the piston.

[0014] When there are two or an even number of cylinders (pistons), the pair of pistons can be moved in opposite directions to cancel out the vibrations caused by the reciprocating motion of the pistons, resulting in an air compressor with less vibration.

[0015] In low-pressure applications where the discharge pressure is 0.2 MPa or less, a motor with the same capacity can have a larger discharge capacity than a compressor with a discharge pressure of 0.8 MPa. In this case, if the cylinder diameter is increased with a conventional crank-piston mechanism, the rider ring length must be increased to accommodate this (L1 in Figure 13). However, with this invention, even if the cylinder diameter is increased with the same two cylinders, stable piston movement is possible without increasing the rider ring length, making it easy to increase the capacity structurally (Figure 10).

[0016] When the discharge pressure is around 0.8 MPa, single-stage compression is used, and the two cylinders shown in Figure 9 have the same diameter. The motor capacity corresponds to 3.7 kW to 7.5 kW.

[0017] When the discharge pressure is 0.8 MPa or more, a two-stage compression system as shown in Figure 11 is applied.

[0018] For larger capacities, a four-cylinder compressor is used, as shown in Figure 12. In this type, the PU1 unit and PU2 unit each cancel out vibrations independently, resulting in a low-vibration compressor overall.

[0019] In the case of a small-capacity air compressor with one cylinder (Fig. 1), the limit for the number of cylinders was about four for a conventional air compressor with a crank-piston mechanism, but with the same number of cylinders it is possible to make it compact as shown in Figs. 25 and 27, and with eight cylinders it can be made eight as shown in Figs. 26, 27 and 28 or as shown in Fig. 30. Furthermore, the number of cylinders can be increased to eight for the types in Figs. 26, 27 and 28, and to 16 for the types in Figs. 31, 32 and 33. This makes it possible to provide air-cooled, large-capacity air compressors.

[0020] For example, as mentioned above, the number of cylinders in a conventional air compressor using a crank-piston mechanism was limited to about four, but in the present invention, it is possible to increase the number to eight. Therefore, an air compressor using a crank-piston mechanism with a motor capacity of 11 kW can be increased to a motor capacity of 22 kW in the present invention.

[0021] Increasing the number of cylinders makes it possible to increase the cooling area for the same motor capacity, which increases cooling capacity and leads to improved performance.

[0022] Conventional pistons are free to rotate around the bearings and are not constrained, so the rider ring needs to be about 60 to 70 percent of the piston diameter. This means that the piston must also be long to ensure stable movement (L1 in Figure 13). This means that the piston must also be long, which increases its mass.

[0023] In a conventional piston, the connecting rod pushes the piston up at an angle (shown as F in Figure 13), which generates lateral pressure (shown as Fs in Figure 13) that pushes against the sides of the cylinder at the same time as compression. This force Fs causes the rider ring, which is responsible for the sliding motion, to slide against the inside of the cylinder, causing wear on the outer surface of the rider ring.

[0024] In contrast, with an integrated connecting rod piston, the connecting rod and piston are integrated into one unit and supported by the rider ring and connecting rod bearing, allowing for approximately linear reciprocating motion, so almost no side pressure Fs is generated. Also, because the piston rotates around the bearing at the end of the connecting rod, the integrated connecting rod piston provides stable approximately linear reciprocating motion while also providing an extremely long rider ring life (Figures 15 and 16). Therefore, stable motion is possible even if the rider ring 72 is short.

[0025] The piston structures shown in Figures 15 to 21 were made possible by eliminating the piston pin, ensuring sufficient space for piston rings, and by the approximately linear reciprocating motion of the connecting rod and piston. This provides a sufficient seal, improving the sealing effect and contributing to increased mechanical efficiency.

[0026] In the case of a fuel-lubricated type, this can be achieved by following the procedures shown in Figures 22 to 24. [Brief explanation of the drawings]

[0027] In the case of oil-free air compressors, rider rings are used as sliding materials. In the case of oil lubrication, rider rings are not used, and an oil film is formed by leaving a gap between the cylinder and piston (Figures 22, 23, and 24). [Figure 1] 1 is a front cross-sectional view of a first embodiment of a swing-type air compressor with a drive / compression integrated housing according to the present invention; [Figure 2] FIG. 1 is a longitudinal sectional view of a first embodiment of a swing-type air compressor with a drive / compression integrated housing according to the present invention, taken along lines ABCDEF. [Figure 3] 1 is a diagram showing the configuration of a four-bar link mechanism used in the drive / compression integrated housing according to the present invention, where the length of each link is a provisionally determined length. [Figure 4] The diagram shows the state when the drive arm and crank radius ab are aligned in the configuration of Figure 3 and the piston of Figure 6 reaches bottom dead center. [Figure 5] In the configuration of Figure 3, the position of crank pin b is rotated 180° from Figure 4, that is, ab and bc are aligned, and the piston of Figure 6 is at top dead center. [Figure 6] FIG. 2 is a diagram showing the state in which a four-bar link is incorporated in the embodiment of FIG. 1 of the swing-type air compressor with a drive / compression integrated housing according to the present invention. [Figure 7]The diagram shows the relationship between the driven arm and the piston integrated with the connecting rod of the present invention. 1. From the center position to the center of the cylinder: 121.85 mm. 2. Oscillating arm length: 123.7 mm. 3. Connecting rod length (from the center of the bearing to 1 / 2 the length of the rider ring). 4. Under the above conditions, the connecting rod-integrated piston oscillation angle is 0.61°. [Figure 8] 7 is a diagram showing the relationship between the driven arm and the piston integrated with the connecting rod of the present invention. When the length of the piston integrated with the connecting rod in FIG. 7 is 200 mm, the oscillation angle is 0.53°. [Figure 9] A front cross-sectional view of a second embodiment of a drive / compression integrated housing according to the present invention, which has two cylinders of the same diameter. [Figure 10] FIG. 10 is a front cross-sectional view of the embodiment shown in FIG. 9 in which two cylinders of the same diameter are used and the diameter is larger. [Figure 11] FIG. 10 is a front cross-sectional view of a second embodiment in which two-stage compression is performed using different diameter cylinders. [Figure 12] A front cross-sectional view of a third embodiment of the driving / compression integrated housing according to the present invention, which has four cylinders of the same diameter. [Figure 13] Cross-sectional view showing the lateral pressure of a typical conventional crank-piston mechanism [Figure 14] A diagram to explain the lateral pressure of a typical conventional crank-piston mechanism [Figure 15] FIG. 1 is a cross-sectional view of the piston ring and rider ring of the piston part of the connecting rod integrated type of the present invention, in which the piston ring is arranged in two stages. [Figure 16] FIG. 1 is a cross-sectional view of the piston ring and rider ring of the piston part of the connecting rod integrated type of the present invention, in which the piston ring is arranged in three stages. [Figure 17] A diagram showing the case where the piston part of the connecting rod integrated with the present invention is a cup seal. [Figure 18] This is a diagram of the case where the piston part of the connecting rod integrated with the present invention is made into a cup seal, and the cup seal is made into two stages. [Figure 19] A diagram showing the case where the piston part of the connecting rod integrated with the present invention is a cup seal and piston ring. [Figure 20] This is a diagram showing the case where the piston part of the connecting rod integrated with this invention is made up of a cup seal and piston ring, and the cup seal is made into two stages. [Figure 21] This is a diagram showing the case where the piston part of the connecting rod integrated with the present invention is made up of a cup seal and a piston ring, and the cup seal and piston ring are arranged in two stages. [Figure 22] In the case of an oil-lubricated engine, if the angle of the connecting rod is tilted by 0.5°, the gap will be 0.1 mm, the same as when there is no tilt. This diagram shows that the radius of the outer spherical surface of the piston should be 1420 mm. [Figure 23] This is a diagram showing the details of the piston part in Figure 22 for the oil-filled type. The piston part length is 50 mm. [Figure 24] Enlarged view of the gap between the piston and cylinder at part D in Figure 23 for the oil-lubricated type. [Figure 25] FIG. 10 is a cross-sectional view of four cylinders in a fourth embodiment of the drive unit / compression unit separated type of the present invention. [Figure 26] FIG. 10 is a cross-sectional view of an eight-cylinder compression unit according to a fourth embodiment of the present invention, in which the drive unit and compression unit are separated. [Figure 27] 10A and 10B are longitudinal cross-sectional views of four- and eight-cylinder compression units according to fourth and fifth embodiments of the present invention, each having a separate compression unit. [Figure 28] 10A and 10B are longitudinal cross-sectional views of four- and eight-cylinder drive units according to fourth and fifth embodiments of the drive unit / compression unit separation type of the present invention. [Figure 29] FIG. 25 shows the state in which a four-bar link is incorporated in the swing-type air compressor having a separate housing for the drive unit and compression unit according to the present invention. [Figure 30] FIG. 10 is a cross-sectional view of eight cylinders in a sixth embodiment of the drive unit / compression unit separated type of the present invention. [Figure 31] FIG. 10 is a cross-sectional view of a 16-cylinder drive unit / compression unit according to a seventh embodiment of the present invention, in which the drive unit and compression unit are separated. [Figure 32]10A and 10B are longitudinal cross-sectional views of the 8- and 16-cylinder compression units of the sixth and seventh embodiments of the drive unit / compression unit separation type of the present invention. [Figure 33] 10A and 10B are longitudinal cross-sectional views of the drive units of the 8- and 16-cylinder types of the sixth and seventh embodiments of the present invention, each having a separate drive unit and compression unit. [Figure 34] 30 and 31 of the embodiment of the swing-type air compressor with a drive unit and compression unit separated housing according to the present invention, showing the state in which a four-bar link is incorporated. DETAILED DESCRIPTION OF THE INVENTION

[0028] 1 to 8, an embodiment of the oscillating oil-free compressor according to the invention will be described. When the drive unit and compression unit are housed in the same housing, they are attached to the pin portion 16a of the crankshaft 16 with bearings 15c and 15d already attached to the big end 15a and small end 15b of the connecting rod 15, respectively.

[0029] The drive section has a bearing housing 10 mounted in a through hole 9c in the lower side surface 9a of a housing 9 having a required volume, and a crankshaft 16 passes through a bearing 10b mounted in the through hole 10a of the bearing housing 10 and a bearing 9g mounted in the other through hole 9f of the housing 9, with the input side 17 of the crankshaft to which a connecting rod is attached projecting outward from the bearing housing 10.

[0030] The pin 12a passes through the through-hole 11b of the driving-side arm portion 11a of the swing arm 11 via the small-end bearing 15d, and similarly the pin 12b passes through the through-hole 11d of the driven-side arm portion 11c via the bearing 13d of the piston 13 that is integral with the connecting rod.

[0031] The swing shaft 14 passes through the bearings 9h and 9i in the through-hole 9d on both upper side surfaces 9a of the housing 9 and penetrates the hole 11e of the swing arm 11.

[0032] A big end bearing 15c of the connecting rod is connected to a pin 16a of the crankshaft, and a small end bearing 15d of the connecting rod is connected to a pin 12a of the drive side arm portion 11a of the swing arm 11. A four-bar link mechanism is formed by the swing arm 11 and the swing shaft integrated with the swing arm 11, and the swing arm 11 is caused to swing by the rotational movement of the crankshaft 16.

[0033] A cover 18a is attached to the surface of the crankshaft opposite the bearing housing, and covers 18b and 18c are attached to both side surfaces 9a of the swing shaft.

[0034] A piston ring 13b and a rider ring 13c are provided on a piston portion 13a of a piston 13 integrated with a connecting rod within the cylinder 7, and the piston portion 13a of the piston 13 integrated with the connecting rod is slidably fitted into a hole 7a of the cylinder 7 and is attached integrally to the housing upper surface 9b.

[0035] A valve plate 5 having an intake port 5d with an intake valve 5c and an outlet port 5b with an outlet valve 5a is integrally provided on a cylinder 7, and a valve cover 1 having an intake port 1b and an outlet port 1a is attached integrally to the valve plate 5.

[0036] A piston 13 integral with a connecting rod having piston rings 13b and rider ring 13c is slidably fitted into the hole 7a of the cylinder 7, and a piston portion 13a is supported to form a four-bar link mechanism, which converts the rotational motion of the crank into an approximate reciprocating linear motion of the piston 13 integral with the connecting rod, thereby performing compression motion.

[0037] In FIG. 7, the length of the swing arm portion 11c is shown as 123.7 mm, and the length of the piston integrated with the connecting rod is shown as 175 mm, but in FIG. 8, the length of the swing arm portion 11c is shown as 123.7 mm, the same as in FIG. 7, and the length of the piston integrated with the connecting rod is shown as 200 mm. As can be seen from Figures 7 and 8, if the length of the connecting rod and piston is 200 mm without changing the length of the arm, and the connecting rod and piston have a stroke of 60 mm, half the oscillation angle of the connecting rod and piston will change from 0.61° to 0.53°. This shows that if the length of the arm and the length of the connecting rod and piston are increased, the oscillation angle of the connecting rod and piston will decrease. In other words, the longer the arm, the smaller the oscillation angle, and the longer the connecting rod, the smaller the oscillation angle of the connecting rod itself. Understanding this and considering actual cases will lead to better products. The correspondence between the four-bar link mechanism abcd shown in FIGS. 3 to 5 and the compressor structure is shown by abcd in FIG.

[0038] 25 to 29, an embodiment of an oscillating type air compressor according to claim 5 will be described. The drive unit A has a drive unit housing 45 having a required volume, and includes a connecting rod 48 mounted on a crank pin 50d via a big end bearing 48b through both side surfaces 45a of the drive unit housing 45, through holes 45b in 45a, bearings 51b in 51, through holes 51d in 45a, and bearings 51c in 51d, and is provided with a crankshaft 50.

[0039] Install the crank bearing housing 51.

[0040] A follower arm 52 is attached to the swing shaft 47 at a predetermined position, and is provided in the compression unit via bearings 41a, 41a in through holes 41b, 41b in the compression unit housing 41.

[0041] A piston ring 13b and a rider ring 13c are attached to a piston portion 13a of the piston 13 that is integral with the connecting rod. A driven arm pin 53 is attached to a through hole 52c of the driven arm via a bearing 13d in through holes 13e, 13e of the piston 13 that is integral with the connecting rod, and pins 53a and 53b are connected to holes in the driven arms 52a and 52b via bearings.

[0042] The piston 13, which is an integral part of the connecting rod, is inserted into the cylinder 7, which has cooling fins around it, and then fitted into the through-hole 41c of the compression unit housing. This is done for a total of four locations: the upper parts U1 and U2 and the lower parts U3 and U4 of the compression unit.

[0043] A valve plate 5 having an intake port 5d with an intake valve 5c and an outlet port 5b with an outlet valve 5a is integrally provided on the cylinder 7 of the compression unit U, and a valve cover 1 having an intake port 1b and an outlet port 1a is provided on the valve plate 5 to form compression units U1 to U4.

[0044] The connecting flange 44 is fitted into the through hole 44c of the compression unit housing and attached, and the swing shaft 47 is assembled via the connecting flange bearing housings 47a, 47a and the bearings 44a in the bearing housings 47a.

[0045] The drive arm 46 is attached to the swing shaft protruding from the connecting flange bearing housing 47a. and then attach the drive arm pin 46a to the drive arm pin hole 46b via the connecting rod small end bearing 48d.

[0046] The swing shaft bearing housing 54a is attached to the swing shaft 47 through the drive unit housing through holes 45d, 45d via bearings 54b.

[0047] The swinging movement of the swing shaft 47 causes the swing arm 52 to swing, causing the connecting rod-integrated piston 13 to perform an approximately linear reciprocating motion, thereby obtaining a required effective compression action.

[0048] Figure 26 is a cross-sectional view of the drive unit and compression unit in the case of an eight-cylinder engine, but an eight-cylinder engine can also be configured as shown in Figure 30. Figure 32 shows a longitudinal cross-sectional view of the compression unit in Figure 30, and Figure 33 shows a longitudinal cross-sectional view of the drive unit.

[0049] Fig. 31 is a cross-sectional view of the drive unit and compression unit in the case of 16 cylinders, Fig. 32 is a longitudinal cross-sectional view of the compression unit in Fig. 31, and Fig. 33 is a longitudinal cross-sectional view of the drive unit.

[0050] In this way, increasing the number of cylinders can increase the amount of air, but on the other hand, if we increase the cooling area of ​​the cylinder without increasing the amount of air, we can increase the cooling capacity without raising the temperature inside the cylinder, which will lead to a longer lifespan of the compressor and ultimately improve reliability.

[0051] The correspondence between the four-bar link mechanism abcd shown in FIGS. 3 to 5 and the compressor structure in FIG. 25 is shown by abcd in FIG.

[0052] As shown in FIGS. 9 to 12, the swing arm 11 in FIG. 1 may be formed with a plurality of (here, two) driven arm portions 11c, so that the pistons 13 of the pair of cylinders 7 reciprocate in opposite directions.

[0053] Next, the piston structure will be described with reference to FIGS. In the piston with an integral connecting rod of the present invention, the piston and connecting rod move together as a unit, performing approximately linear reciprocating motion. The absence of a piston pin allows for effective use of the space. The fact that the piston with an integral connecting rod is integrated and performs approximately linear reciprocating motion as a unit, and the absence of a piston pin allows for effective use of the space, makes it possible to create the following piston seal. This is described below. Figures 15 to 21 describe an oil-free air compressor, while Figures 22 to 24 describe an oil-type air compressor. 1) Two PTFE-based piston rings (71) act as an air seal. The PTFE-based rider ring (72) acts as a sliding member to prevent the metal of the piston from coming into direct contact with the cylinder (Figure 15). 2) Three stages of PTFE-based piston rings (71) act as an air seal. The PTFE-based rider ring (72) acts as a sliding member to prevent the metal of the piston from coming into direct contact with the cylinder (Figure 16). 3) A single-stage PTFE ring 82 is provided. This cup-shaped seal functions as a seal and also as a sliding member (Figure 17). 4) A two-stage ring 82 made of PTFE or similar material. This cup-shaped seal functions as a seal and also as a sliding member (Figure 18). This is intended to improve the sealing effect and durability at the same time. 5) 71 piston rings made of PTFE or other materials are used in one stage to seal the air. A single stage of PTFE ring 82 is provided. As mentioned above, the cup-shaped ring serves as both a seal and a sliding member (Fig. 19). 6) 71 piston rings made of PTFE or other materials are used in one stage to seal the air. Two tiers of PTFE rings 82 are provided. As mentioned above, the cup-shaped rings serve as both seals and sliding members (Figure 20). 7) Two stages of 71 piston rings made of PTFE or other materials are used to seal the air. Two stages of PTFE rings 82 are provided. As mentioned above, the cup-shaped rings serve as both seals and sliding members (Fig. 21). 8) In the case of oil lubrication, the piston is lubricated by providing a certain gap between the piston and the cylinder, filling the gap with lubricating oil to form an oil film. Figure 22 shows the overall view, while Figure 23 shows an enlarged view of the piston that is integrated with the connecting rod. Figure 24 shows an even larger view of the relationship between the piston and cylinder. The values ​​shown in the figures are only examples.

[0054] Higher sealing performance means higher mechanical efficiency for the air compressor, which contributes to energy savings.

[0055] Next, we will explain the structure with cylinders arranged on the left and right sides of the crankshaft with reference to Figures 30 to 33. Figure 30 shows the structure of Figure 25, but with the cylinders arranged symmetrically around the crankshaft. In other words, while the cross-sectional view of Figure 25 shows two cylinders arranged around the oscillating axis, the longitudinal cross-sectional view of Figure 27 shows four cylinders arranged symmetrically above and below the oscillating axis. From these two cross-sectional views, we can see that there are four cylinders. Furthermore, the cross-sectional view of Figure 30 and the longitudinal cross-sectional view of Figure 32 show four cylinders arranged on the right side and four on the left side of the crankshaft. Therefore, the total number of cylinders is eight. As a result, assuming the displacement volume of each cylinder is the same, this compressor structure has the capacity to discharge eight times the volume of a compressor with one cylinder. Figure 33 shows a longitudinal cross-sectional view of the drive unit.

[0056] Looking at the cross section in Figure 26, we can see that there are four cylinders. Looking at the longitudinal section in Figure 27, we can see that there are four cylinders. Therefore, we can see that the total number of cylinders is eight. Furthermore, looking at Figure 31, we can see that the total number of cylinders is 16, just like (0055). As a result, if the displacement volume of each cylinder is the same, we can see that a compressor with this structure has the capacity to discharge 16 times the volume of a compressor with one cylinder. Figure 33 shows a longitudinal section of the drive unit.

[0057] In this way, one drive unit can operate multiple cylinders. 1) Whereas in the past two or more units had to be prepared for the same discharge volume, the compressor of the present invention can be configured as shown in Figure 26 or Figure 30, with only eight cylinders in either case. Reducing the number of units used makes it possible to reduce the installation area, which further leads to cost reduction. 2) Furthermore, by adopting the large-capacity model shown in Figure 31, it is possible to achieve further cost reductions. 3) By utilizing the large capacity, the rotation speed can be reduced, extending the life of the compressor. It will be possible to extend the period. It is believed that there are other applications that take advantage of the advantages of the present invention, such as the above. [Explanation of symbols]

[0058] A drive unit; B compression unit; D. Enlarged piston spherical surface; PIN Piston pin; PU1 Compression Unit 1; PU2 Compression Unit 2; U1 First Compression Unit; U2 Second Compression Unit; U3 Third compression unit; U4 fourth compression unit; LP connecting rod length; RA: radius of driven arm; 1 valve cover; 1a valve cover outlet; 1b Valve cover intake; 5 valve plates; 5a discharge valve a; 5b discharge valve a discharge port; 5c intake valve c; 5d intake valve c intake port; 7 cylinders; 7a cylinder inner circumference; 9 Housing; 9a Both sides of the housing; 9b Top of housing; 9c bearing housing mounting hole; 9d swing shaft bearing mounting hole; 9f Housing B side crankshaft bearing through hole; 9g Housing b side crankshaft bearing; 9h·9i Swing shaft bearing; 10 crankshaft bearing housing; 10a crankshaft bearing through hole; 10b crankshaft bearing; 11 swing arm part; 11a drive arm part; 11b Drive arm pin through hole; 11c driven arm part; 11d Follower arm pin through hole; 12a Drive arm pin; 12b Follower arm pin; 13 Connecting rod and piston; 13a Piston of a piston with integral connecting rod; 13b piston rings; 13c Rider Ring; 13d Connecting rod integral piston bearing; 13e Connecting rod integral piston lower end; 14 Swing axis 1; 15 Connecting rod 1; 15a Connecting rod big end bearing through hole; 15b Connecting rod small end bearing through hole; 15c Connecting rod big end bearing; 15d Connecting rod small end bearing; 16 crankshaft; 16a crankpin; 17 crankshaft input shaft; 18a cover plate a; 18b cover plate b; 18c cover plate c; 41 Compression section housing; 41a Swing shaft bearing; 41b compression section housing through-hole b; 41c compression section housing through-hole c; 44 connecting flange; 44a Coupled flange bearing; 44b Connecting flange bearing through hole; 44d Connecting flange bearing fitting hole d; 45 drive housing; 45a Drive housing both sides; 45b Drive housing through hole b; 45c Drive housing through hole c; 45d Drive housing through hole d; 46 drive arm; 46a drive arm pin; 46b Drive arm pin through hole; 47 Swing axis 2 47a Swing shaft bearing housing; 47b swing shaft through hole; 48 conrod 2; 48a Connecting rod big end; 48b Connecting rod big end bearing; 48c connecting rod small end; 48d Connecting rod small end bearing; 50 crankshaft; 50a crankshaft input; 51 crankshaft bearing housing; 51a crankshaft bearing housing through hole; 51b crankshaft bearing b; 51c crankshaft bearing c; 51d crankshaft bearing c through hole; 52 driven arm; 52a driven arm a; 52b driven arm b; 52c Follower arm through hole; 53 Follower arm pin; 53a Follower arm pin a; 53b Follower arm pin b; 54a swing shaft bearing housing 2; 54b swing shaft bearing housing 2 bearing; 54c swing shaft bearing housing 2 through hole; 54d cover plate d; 54e Cover plate e; 61 8-cylinder compression unit housing; 66 8·16 Cylinder drive unit housing; 71 Piston rings for connecting rod-integrated pistons; 72 Rider ring of connecting rod and piston; 81 seal retainer; 82 cup seals; 84 seal holder; 86 Piston ring holder 1; 87 Piston ring holder 2;

Claims

1. a crankshaft passing through a housing via a bearing, a drive-side connecting rod provided on a crank pin of the crankshaft via a large-end bearing, a drive-side pin provided on the drive-side connecting rod via a small-end bearing, and a swing arm having one end and the other end, one end of which is connected to the drive-side pin and a swing shaft passing through the housing at its middle, the swing arm having a drive-side swing arm portion and a driven-side swing arm portion; a piston that is integral with a driven connecting rod connected via a bearing to a driven pin provided at the other end of the swing arm, the piston having piston rings around its upper and lower ends, respectively, and that does not have a piston pin and is slidably fitted into a cylinder of the compression unit; a cylinder having cooling fins formed around its periphery and integrally provided on an upper portion of the housing; a valve plate having an intake port with an intake valve and an outlet port with a discharge valve and integrally provided on the cylinder; and a valve cover having an intake port and an outlet port and integrally provided on the valve plate; An oscillating air compressor in which an oscillating arm is oscillated via the small end of a driving connecting rod connected to a crankshaft, and the other end is connected to a connecting rod portion bearing of a piston integral with the connecting rod within the housing, and the rotational movement of the crank is converted into oscillating motion by a four-bar link mechanism, causing the piston to move back and forth via a driven connecting rod connected to the other end of the oscillating arm.

2. 2. The oscillating air compressor according to claim 1, wherein the other end of the oscillating arm or the driven oscillating arm portion is caused to make a linear reciprocating motion approximately in the direction of the linear reciprocating motion of the piston by the rotational motion of the crankshaft.

3. 2. The oscillating air compressor according to claim 1, wherein the driven-side oscillating arm portion is connected to the connecting rod of the piston in a substantially perpendicular or orthogonal state.

4. 2. The oscillating air compressor according to claim 1, wherein the driven-side oscillating arm portion is connected to the connecting rod so as to be perpendicular to the connecting rod of the piston when the piston is positioned at the middle of its reciprocating stroke.

5. a drive unit having a crankshaft passing through a drive unit housing via a bearing, a drive unit side connecting rod attached to a crank pin of the crankshaft via a large end bearing, a drive unit side pin attached to the drive unit side connecting rod via a small end bearing, a drive unit side swing arm connected to the drive unit side pin, and a swing shaft passing through the swing arm and into the housing; a first compression unit having cooling fins on the periphery and a cylinder with an opening formed in the center inside the middle part; a second compression unit having cooling fins around the periphery and a cylinder with an opening at the center inside the middle part, the second compression unit having a compression unit housing formed symmetrically with the first compression unit about the swing axis; a valve plate having an intake port with an intake valve and a discharge port with a discharge valve, the valve plate being integrally provided on a cylinder of the first compression unit; and a valve cover having an intake port and a discharge port, the valve plate being integrally provided; a piston having piston rings around its upper and lower ends, respectively, and integrally provided with a connecting rod having no piston pin and slidably provided within the cylinder of the first compression unit; a first compression unit housing provided integrally with the swing shaft and having a driven-side swing arm portion connected at one end to both of the driven-side connecting rods; a piston having piston rings around its upper and lower ends, respectively, and integrally provided with connecting rods each having no piston pin and each slidably fitted in a cylinder of the second compression unit; a second compression unit housing having a swing shaft provided horizontally at the center between the two compression unit housings, and a driven-side swing arm portion provided integrally with the swing shaft, the other end of which is connected to both of the driven-side connecting rods; a connecting flange for concentrically connecting the centers of the swing shafts connecting the compression unit housing and the drive unit housing; a lower end of a piston with an integral connecting rod in the first compression unit connected to one end of the driven swing arm, and a lower end of a connecting rod of a piston with an integral connecting rod in the second compression unit connected to the other end of the driven swing arm; and a four-bar link mechanism converts the rotational movement of the crank into swinging movement to swing the driven swing arm, thereby reciprocating the piston via the driven connecting rod connected to both ends of the driven swing arm.

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