JP2011220287A5 - - Google Patents

Description

In order to solve the above-described problems, a reciprocating compressor according to the present invention has a low-pressure side piston and a low-pressure side cylinder, and the low-pressure side piston reciprocates while swinging in the low-pressure side cylinder. and the low-pressure side compression unit for compressing, and a high pressure side piston and the high pressure side cylinder, the high pressure side piston is compressed by the low pressure side compression portion by reciprocating while swinging in the high pressure side cylinder A reciprocating compressor comprising a high-pressure side compressor that further compresses air, and a motor that drives the low-pressure side compressor and the low-pressure side compressor, the maximum inclination angle when the low-pressure side piston swings. The high-pressure side piston is made larger than the maximum inclination angle at the time of swinging.

A reciprocating compressor according to another aspect of the present invention includes a motor having a rotation shaft, a low-pressure side cylinder, and a low-pressure side piston, and compresses air, a high-pressure side cylinder, and a high-pressure side piston. with the door, said a low pressure side reciprocating the compressor and a high pressure side compression unit further compressing the compressed air in the compression unit, each of the low-pressure side piston and the high pressure side piston of the rotary shaft of the motor and eccentric to perform an eccentric motion with rotation, the connecting rod extending from said eccentric, and a piston body which is provided at the distal end of the connecting rod, eccentricity with respect to the eccentric axis of rotation of the motor of the low-pressure side piston Is r1, and r1> r2 where r2 is the amount of eccentricity of the high-pressure side piston relative to the rotational shaft of the eccentric motor. Is characterized in that said forming said low-pressure side piston and the high pressure side piston as.

Next, it demonstrates, referring the enlarged view of the high voltage | pressure side compression part shown in FIG.
The lip ring 6, the lip ring 9 and the piston ring 10 are formed in a substantially annular shape by a resin material excellent in wear resistance and self-lubricating property. The piston ring 10 has a substantially rectangular cross section and a constant radial width over the entire circumference. Further, the piston ring 10 is formed with an abutment portion (not shown) in the circumferential direction thereof, so that the diameter can be enlarged and reduced while maintaining the sealing performance by the abutment portion. In addition, the piston ring 10 has an inner diameter in a state where the piston ring 10 is in contact with an inner peripheral surface of a high-pressure side cylinder 17 described later when the high-pressure side piston 8 is at the top dead center position or the bottom dead center position. The diameter is larger than the minimum diameter of the piston ring groove, which is the groove in the portion where the is mounted. Thereby, the piston ring 10 can be moved in the radial direction with respect to the piston 8 on the high pressure side.

The lip ring 9 is mounted in a direction opposite to the lip ring 6 (direction in which the skirt portion faces the crankcase side). By mounting in this direction, the centers of the lip ring 9 and the piston body 11 coincide. Further, when the cylinder 17 is assembled to the crankcase 1, the lip ring 9 comes into contact with the inner wall surface of the cylinder 17 and determines the assembly position of the cylinder 17. Therefore, the centers of the cylinder 17 and the piston body 11 coincide. As a result, the piston ring 10 mounted on the piston body 11 and the cylinder 17 can be centered. Furthermore, the lip ring 9, it is possible to the piston ring 10 to prevent contact between the piston body 11 and the cylinder 17 when worn, can improve the life of the piston main body 11 and the cylinder 17. Further, by sandwiching the lip ring 9 between the base 11A and the connecting rod 8A, it is possible to prevent the compression heat generated in the cylinder 17 from being transmitted from the piston body 11 to the connecting rod 8A, and to increase the temperature of the large end portion. Can be reduced. As a result, it is possible to improve the life of the bearings provided on the outer circumferences of the eccentrics 7 and 13.

Here, in the two-stage compressor of Patent Document 2, in the high-pressure side and the connecting rod have employed reciprocating piston structure connected to the piston via a needle bearing, needle bearing in this embodiment of the present invention The locking piston mechanism that integrally forms the connecting rod and the piston body is eliminated, improving durability by reducing moving parts, reducing weight and noise, and reducing costs by reducing the number of parts. did.

In an embodiment of the present invention in view of the above, the low-pressure side of the piston 4 and the high pressure side of the piston 8 the connecting rod 4A, 8A and piston body 5 (11) and integrally forming a connecting rod 4A, 8A The piston main body 5 (11) is inclined together with the connecting rods 4A and 8A when the cylinder is inclined, and the piston main body 5 (11) reciprocates while swinging in the cylinders 14 and 17, and the low pressure side piston 4 And the high-pressure side piston 8 were designed in consideration of the angle at which they were inclined in the cylinders 14 and 17, respectively.

Here, especially in the case of a portable air compressor that is carried, balance of the center of gravity of the product is important. As shown in FIG. 3, the portable air compressor is, for example, on (approximately the center of) a pair of air tanks 22. 1, the compressor main body 21 including the low-pressure side compression unit and the high-pressure side compression unit and the motor 3 are mounted, and each auxiliary component, particularly the pressure reducing valve 23 (26) and the pressure gauge 24 (27 having a large mass). ), The air take-out coupler 25 (28) is mounted so as to be symmetric with respect to the compressor main body 21, thereby providing a layout considering the balance of the center of gravity of the product.

As shown in FIG. 4, the piston 4 (8) and the connecting rod 4A (8A) are connected to the connecting rod 4A (8A) while the connecting rod 4A (8A) is moving toward the top dead center and the bottom dead center in the suction and discharge processes. ) is obliquely against the central axis of the cylinder 14 (17) by the eccentricity of the eccentric 7 (13).

l：連接棒長さ
ｒ：偏心量（＝ストロークＳ／２） The maximum inclination angle when the piston 4 (8) swings with respect to the cylinder 14 (17) will be described. Here, at the time the piston 4 (8) swings cylinder 14 (17) within the maximum angle at which the longitudinal axis is inclined connecting rods 4A against the cylinder center axis (8A), or against the cylinder center axis When the inclination angle θ is the maximum angle at which the upper surface of the piston attached to the upper side of the imaginary plane perpendicular to the connecting rod and the connecting rod is inclined, the inclination angle θ is calculated by the following equation (1 4 ). The length (the length from the center of the eccentric 7 (13) to the tip (upper surface) of the piston body 5 (11)) l and the eccentric amount r of the eccentric 7 (13) with respect to the shaft 2 of the motor 3 are determined.

l: Connecting rod length r: Eccentricity (= stroke S / 2)

Way to the suction and discharge concatenated in step rods 4A (8A) is the top dead center and bottom dead center, the connecting rod 4A (8A) is against the central axis of the cylinder 14 (17) by the eccentricity of the eccentric 7 (13) It becomes diagonal. At this time, the shape of the contact surface between the lip ring 6 (piston ring 10) and the cylinder 14 (17) is an elliptical shape whose major axis is the swing direction (left-right direction in FIG. 4) (viewed from above the central axis of the cylinder). Therefore, it is easy to create a gap between the swing direction side 6A (9A) of the lip ring 6 (piston ring 10) and the cylinder 14 (17). Leakage from the gap could cause performance degradation.

1 ... Crankcase 2 ... Shaft (Rotating shaft)
3 ... Motor 4 ... Piston (low pressure side)
4A ... Connecting rod (low pressure side)
5. Piston body (low pressure side)
5A ... Retainer 6 ... Lip ring (low pressure side)
7 ... eccentric (low pressure side)
8 ... Piston (high pressure side)
8A ... Connecting rod (high pressure side)
9 ... Lip ring (high pressure side)
10 ... Piston ring 11 ... Piston body (high pressure side)
11A ... Base 12 ... Top 13 ... Eccentric (high pressure side)
14 ... Cylinder (low pressure side)
15 ... Air valve (low pressure side)
16 ... Cylinder head (low pressure side)
17 ... Cylinder (high pressure side)
18 ... Air valve (high pressure side)
19 ... Cylinder head (high pressure side)
20 ... Cooling fan 21 ... Air tank 22 ... Compressor body 23 ... Pressure reducing valve (low pressure side)
24 ... Pressure gauge (low pressure side)
25 ... Coupler (low pressure side)
26 ... Pressure reducing valve (high pressure side)
27 ... Pressure gauge (high pressure side)
28 ... Coupler (high pressure side)

Claims (16)

A low pressure side piston and a low pressure side cylinder, and the low pressure side piston compresses air by reciprocating while swinging in the low pressure side cylinder; and
And a high voltage side piston and the high pressure side cylinder, the high pressure side piston the high side pressure compressing section for the further air compressed in the low pressure side compression unit compressing the by reciprocating with swing cylinder When,
A reciprocating compressor and a motor for driving the low-pressure compressing section and the high pressure side compression unit,
A reciprocating compressor characterized in that a maximum inclination angle when the high pressure side piston swings does not become larger than a maximum inclination angle when the low pressure side piston swings. Maximum gap generated between the high pressure side piston and the high pressure side cylinder during oscillation of the high pressure side piston than the maximum gap generated between the low-pressure side piston and the low pressure side cylinder during oscillation of the low-pressure side piston The reciprocating compressor according to claim 1, wherein the reciprocating compressor does not increase.   The low-pressure side piston and the high-pressure side piston are respectively connected to a rotating shaft of the motor, and include an eccentric that performs a rotational motion, a piston body that compresses air in a cylinder, a connecting rod that connects the eccentric and the piston body. The reciprocating compressor according to claim 1, wherein the piston main body is fixed to the connecting rod.   The reciprocating compressor according to claim 3, wherein the piston body swings in accordance with the eccentric rotational movement.   The reciprocating compressor according to any one of claims 1 to 4, wherein a bore diameter of the high pressure side piston is not made larger than a bore diameter of the low pressure side piston.   The reciprocating compressor according to claim 3, wherein a length from the eccentric center to the tip of the low-pressure side piston is substantially equal to a length from the eccentric center to the tip of the high-pressure side piston. The lip ring is provided in a piston main body that compresses air in the low pressure side cylinder of the low pressure side piston, and the piston ring is provided in the piston main body of the high pressure side piston. The reciprocating compressor described. The piston body is provided in a piston main body for compressing air in the low pressure side cylinder of the low pressure side piston, and the piston ring is provided in the piston main body of the high pressure side piston. The reciprocating compressor described. A motor having a rotating shaft;
A low pressure side compression section that includes a low pressure side cylinder and a low pressure side piston, and compresses air;
A reciprocating same compressor comprising a high pressure side cylinder and a high pressure side piston, and comprising a high pressure side compression part for further compressing the air compressed by the low pressure side compression part,
The low-pressure side piston and the high-pressure side piston each include an eccentric that performs an eccentric motion as the rotation shaft of the motor rotates, a connecting rod extending from the eccentric, and a piston body provided at the tip of the connecting rod. ,
When the eccentricity of the low-pressure side piston with respect to the rotational axis of the motor is r1, and the eccentricity of the high-pressure side piston with respect to the rotational axis of the motor is r2, the relationship is such that r1> r2. A reciprocating compressor characterized by forming a low pressure side piston and the high pressure side piston. Maximum gap generated between the high pressure side piston and the high pressure side cylinder during oscillation of the high pressure side piston than the maximum gap generated between the low-pressure side piston and the low pressure side cylinder during oscillation of the low-pressure side piston The reciprocating compressor according to claim 9, wherein the reciprocating compressor is reduced.   11. The reciprocating compressor according to claim 9, wherein each of the low pressure side piston and the high pressure side piston has a piston body fixed to the connecting rod. It said With the eccentric of the eccentric motion, reciprocating compressor of claim 9, wherein the piston body, characterized in that reciprocates while swinging said high pressure side cylinder and in the low pressure side cylinder.   The reciprocating compressor according to any one of claims 9 to 12, wherein a bore diameter of the high pressure side piston is made smaller than a bore diameter of the low pressure side piston. The length from the eccentric center of the low pressure side piston to the tip of the piston body of the low pressure side piston is 11, and the length from the eccentric center of the high pressure side piston to the tip of the piston body of the high pressure side piston is a reciprocating compressor according to claim 9, wherein the forming the low-pressure side piston and the high pressure side piston such that r1 / l1> r2 / l 2 when the l2.   The reciprocating compressor according to any one of claims 9 to 14, wherein a lip ring is attached to the piston main body of the low pressure side piston, and a piston ring is attached to the piston main body of the high pressure side piston.   The reciprocating compressor according to any one of claims 9 to 14, wherein a piston ring is attached to the piston main body of the low pressure side piston, and a piston ring is attached to the piston main body of the high pressure side piston.

Images