JPH09184494A - Swing compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To optimize designing of compression elements by extending a diameter of a bore of a cylinder chamber by decentering a piston shaft and minimizing cylinder height and decentering quantity of a decentered shaft part. SOLUTION: A piston 9 is arranged by decentering a piston shaft OP to an opposite side of a blade 31 against a shaft center OH of a decentered shaft part 5a so as to extend a bore sectional area of a cylinder chamber 6a, and the piston shaft OP is oscillated by drawing an envelope type oscillating locus at the time of the piston 9 rotating. A shaft center OC of the cylinder chamber 6a is decentered to the opposite side of the blade 31 against a shaft center OK of a drive shaft 5 so as to make an outer peripheral surface 12 of the piston 9 rotate along an inner peripheral wall 11 of the cylinder chamber by following the oscillating locus of the piston shaft. The shaft center of the decentered shaft part, the shaft center of the drive shaft, the piston shaft and the shaft center of the cylinder chamber are respectively provided in order sequentially from the blade side on an advance and retreat moving axis (m) of the blade at a top dead center position of the piston respectively. The outer peripheral surface of the piston is formed in a sectionally round shape, and an inner peripheral wall of the cylinder chamber is formed in a sectionally non-round shape respectively.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swing compressor used for a refrigerating machine or the like, and more particularly to a structure for enlarging a bore cross sectional area of a cylinder chamber.

[0002]

2. Description of the Related Art Generally, this swing compressor is disclosed in, for example, Japanese Unexamined Patent Publication No. 6-58276.
A motor and a compression element driven by the motor are housed in a closed casing. The compression element is arranged in the cylinder chamber and a cylinder having a cylinder chamber in which an intake port and a discharge port are opened, and an inner peripheral portion is rotatably fitted to an eccentric shaft portion of a drive shaft driven by the motor. A piston, a blade radially outwardly coupled to the outer periphery of the piston, and a blade for partitioning the cylinder chamber into a low-pressure chamber communicating with the suction port and a high-pressure chamber communicating with the discharge port; It is provided between the suction port and the discharge port,
A hole having an opening opening in the cylinder chamber and a swingable shaft provided in the hole with a shaft extending in the piston axial direction as a fulcrum, and the projecting tip side of the blade is swingably and forwardly and backwardly supported. An oscillating bush is provided, and the piston revolves along the inner peripheral wall of the cylinder chamber so that the piston oscillates around the oscillating bush via the blade as the drive shaft rotates,
By this revolution, a fluid such as a refrigerant gas sucked from the suction port into the low pressure chamber is compressed to a high pressure, and the high pressure fluid is discharged from the high pressure chamber through the discharge port. In this case, since the drive shaft is driven by the motor located on the centerline of the body of the closed casing, the eccentric shaft portion oscillates eccentrically with respect to the centerline of the body of the closed casing (axis of the drive shaft). The bore of the cylinder chamber is set by the amount of eccentricity of the eccentric shaft portion with respect to the drive shaft while ensuring the bush hole in the inner peripheral portion of the cylinder with the center of the bore aligned with the center line of the body.

On the other hand, as other swing compressors,
Utilizing a configuration unique to swing compressors in which the piston does not rotate, the piston shaft is eccentric to the high pressure rotation region side with respect to the axial center (bore center) of the cylinder chamber so that the high pressure chamber becomes smaller than the low pressure chamber. The axis of the cylinder chamber
In order to revolve the outer peripheral surface of the piston with respect to the inner peripheral surface of the cylinder chamber along with the swing locus of the piston shaft, it is eccentric to the low pressure rotation region side with respect to the axial center of the drive shaft, and in the high pressure rotation region. There is also a system in which the revolution speed of the piston is reduced to reduce overcompression by reducing the speed of the discharged fluid and to reduce the fluctuation of the compression power with respect to the rotation angle (Japanese Patent Laid-Open No. Hei 5-
248379).

[0004]

However, in the swing compressor in which the bore center of the cylinder chamber coincides with the body centerline as described above, the bore diameter of the cylinder chamber is such that the bush hole is secured in the inner peripheral portion of the cylinder. As described above, the amount of eccentricity of the eccentric shaft portion with respect to the center line of the body of the closed casing (the axial center of the drive shaft) is set in a state where the outer diameter of the cylinder is restricted. Therefore, when increasing the bore volume of the cylinder chamber, it is necessary to increase the height of the cylinder chamber in the cylinder axis direction, that is, the cylinder height. However, if the cylinder height is increased, the length in the axial direction of the piston between the inner peripheral surface of the cylinder chamber and the outer peripheral surface of the piston is increased, and the fluid leakage gap between the both surfaces is increased. At the time of processing such as polishing of the inner peripheral surface and the outer peripheral surface of the piston, the processing accuracy deteriorates due to the bending of the processing tool that is inserted from the piston axial direction, and the efficiency of the compressor may decrease. On the other hand, if the cylinder height is increased to increase the bore volume of the cylinder chamber, the eccentricity of the eccentric shaft cannot be minimized.
The blade requires a length in the advancing / retreating direction, and cannot reduce the cost by shortening the processing dimension.

The present invention has been made in view of the above points, and its object is to minimize the cylinder height by effectively eccentricizing the piston shaft to expand the bore of the cylinder chamber. This is to optimize the design of the compression element by minimizing the amount of eccentricity of the eccentric shaft portion.

[0006]

[Means for Solving the Problems] In order to achieve the above-mentioned object, a solution means of the invention according to claim 1 is a suction port (2
1) and a cylinder (6) having a cylinder chamber (6a) with the discharge port (22) opening, and an eccentric shaft portion (5) of the drive shaft (5), which is disposed inside the cylinder chamber (6a). 5a) is rotatably fitted to a piston (9), and a low pressure chamber (34) is connected to the outer periphery of the piston (9) in a protruding manner and connects the cylinder chamber (6a) to the suction port (21). And a high-pressure chamber (35) communicating with the discharge port (22), and a blade chamber (31) provided between the suction port (21) and the discharge port (22) of the cylinder (6). A hole (24) having an opening (24a) opening to (6a) and a shaft (OB) extending in the piston axis (OP) direction in the hole (24) are provided so as to be swingable, and the blade is (31) is provided with a swinging bush (32) that swingably and reciprocally supports the protruding tip side, and the piston (9) is rotated by the drive shaft (5) to rotate the cylinder chamber (6a).
Assume a swing compressor (1) configured to revolve within. Then, the piston (9) is moved to the eccentric shaft portion (5) so as to enlarge the bore cross-sectional area of the cylinder chamber (6a).
Install the piston shaft (OP) with respect to the shaft center (OH) of (a) above the blade (3
Installed eccentrically on the side opposite to 1), and above the piston shaft (OP)
At the center of the eccentric shaft (5a) that swings in a nearly perfect circle around the shaft center (OK) of the drive shaft (5) when the piston (9) revolves.
Swing it so that it draws a trajectory (X) in the form of a line with respect to H). Further, the shaft center (OC) of the cylinder chamber (6a), the outer peripheral surface (12), (12 '), (12'') of the piston (9) the rocking locus of the piston shaft (OP) ( X) along with the inner peripheral surface of the cylinder chamber (6a) (1
1), (11 '), (11'') so as to revolve along the axis (OK) of the drive shaft (5) to the opposite side of the blade (31) and eccentric It was done.

With this configuration, in the invention according to claim 1, the eccentric bush (5a) is used as it is, and the piston (9) is used.
The diameter of the cylinder chamber (6
The bore diameter of a) is expanded to the side opposite to the blade (31), the bore cross section area is expanded without being restricted by the bush hole (hole) in the cylinder inner circumference, and the bore volume of the cylinder chamber is increased. To do.

Therefore, even if the cylinder height is reduced, the bore volume of the cylinder chamber (6a) is secured. By reducing the cylinder height, the inner peripheral surfaces (11), () of the cylinder chamber (6a) are 11 '), (11'') and the outer peripheral surface (12) of the piston (9),
Insert the fluid leak gap between (12 ') and (12'') into the piston shaft (OP).
It is possible to decrease in the direction and cylinder chamber (6a)
When machining the inner peripheral surface (11), (11 '), (11'') of the and the outer peripheral surface (12), (12'), (12 '') of the piston (9), etc.
The bending of the processing tool inserted from the (OP) direction is suppressed, and the processing accuracy of the processing tool is improved. Moreover, piston (9)
By increasing the bore diameter of the cylinder chamber (6a) as the diameter increases, it is also possible to minimize the eccentricity of the eccentric shaft (5a) with respect to the axis (OK) of the drive shaft (5). (31) is reduced in the advancing / retreating direction, and the cost is reduced by shortening the processing size of the blade (31).

The solution taken by the invention according to claim 2 is as follows.
The piston shaft (OP) of the invention according to claim 1 is specified, and the blade (3) is provided on the axis (m) extending in the forward and backward movement direction of the blade (31).
It is configured to be eccentrically provided on the side opposite to 1).

With this configuration, in the invention according to claim 2, the swing locus (X) of the piston shaft (OP) becomes the largest in the radial direction, and accordingly, the bore diameter of the cylinder chamber (6a) expands to the maximum. The diameter is increased and the cross-sectional area of the bore is expanded, and the bore volume of the cylinder chamber (6a) is expanded more effectively.

A solution taken by the invention according to claim 3 is as follows.
In addition to the constituent features of the invention described in claim 1 or 2,
The outer peripheral surface (12) of the piston (9) is formed into a perfect circular cross section centered on the piston shaft (OP), while the inner peripheral surface (11) of the cylinder chamber (6a) is connected to the piston (9). The outer peripheral surface (12) is formed to have a non-circular cross-section that revolves along the swing locus (X) of the piston shaft (OP).

With this configuration, in the invention according to claim 3, by making the outer peripheral surface (12) of the piston (9) a circular cross section, for example, an end mill having the same circular cross section as the piston (9). By swinging the processing tool of (1) along the trajectory of the inclusion line (X) with the piston axis (OP) as the fulcrum, the inner peripheral surface (11) of the cylinder chamber (6a) with a non-circular cross section is formed. Easy to process.

[0013] The solution taken by the invention according to claim 4 is as follows.
In addition to the constituent features of the invention described in claim 1 or 2,
The inner peripheral surface (11 ') of the cylinder chamber (6a) is formed into a perfect circular cross section centered on the axial center (OC) of the cylinder chamber (6a), while the outer peripheral surface (12') of the piston (9) is formed. ) Is configured to have a non-circular cross section that revolves along the inner peripheral surface (11 ') of the cylinder chamber (6a) along with the swing locus (X) of the piston shaft (OP). It is a thing.

With this configuration, in the invention according to claim 4, the inner peripheral surface (11 ') of the cylinder chamber (6a) has a perfect circular cross section which is easy to be machined. 1
The 1 ') side can be easily and accurately processed with a processing tool such as an end mill. On the other hand, pistons that are not restricted during processing
Since the outer peripheral surface (12 ′) side of (9) has a non-circular cross-sectional shape, the outer peripheral surface (12 ′) can be accurately and easily processed into a non-round circular cross-section.

Furthermore, the solution means taken by the invention of claim 5 is, in addition to the constituent features of the invention of claim 1 or claim 2, the outer peripheral surface (12 '') of the piston (9) and the cylinder chamber.
The inner peripheral surface (11 '') of (6a) is the inner peripheral surface (1 '' of the cylinder chamber (6a).
1 ''), the outer peripheral surface (12 '') of the piston (9) is formed to have a non-circular cross section so as to revolve along the swing trajectory (X) of the piston shaft (OP). It is what

With this configuration, in the invention according to claim 5, the inner peripheral surface (11 '') of the cylinder chamber (6a) on the high pressure rotation region side and the low pressure rotation region side, which are substantially orthogonal to the advancing / retreating direction of the blade (31). ) And the outer peripheral surface of the cylinder (6) can be effectively used to efficiently expand the bore diameter of the cylinder chamber (6a), which further increases the bore volume. Expanded.

[0017]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 4 shows the entire structure of the swing compressor according to the embodiment of the present invention. The swing compressor (1) is
A motor (3) is installed in the upper inner part of the closed casing (2), and a compression element (4) is installed on the lower side of the motor (3), and a drive shaft extending from the motor (3). The compression element (4) is driven to rotate at (5). This compression element (4) is a cylinder with a cylinder chamber (6a) inside.
(6) and a front head (7) which is disposed in contact with the upper and lower open portions of the cylinder (6) and closes the upper and lower open portions.
And a rear head (8) and a piston (9) rotatably arranged in the cylinder chamber (6a),
The lower part of the drive shaft (5) is bearing-supported by the bearings provided in (7) and (8).

Further, as shown in FIG. 1, the cylinder chamber
The inner peripheral wall (11) as the inner peripheral surface of (6a) is formed in a substantially circular cross-section, the piston (9) is formed in an annular shape,
An eccentric shaft portion (5a) is rotatably fitted on the inner peripheral side thereof. The shaft center (OH) of the eccentric shaft part (5a) is offset by a predetermined amount (eccentricity) from the shaft center (OK) of the drive shaft (5) on the forward / backward movement axis (m) of the blade (31) described later. It is provided by
When the drive shaft (5) rotates, the piston (9) does not rotate and the inner peripheral wall (1a) of the cylinder chamber (6a)
It revolves along the inner wall (11) while contacting or approaching (1). An oil supply passage (10) opening to the bottom oil sump (2a) of the casing (2) is provided on the shaft center (OK) side of the drive shaft (5). This oil supply passage (10) is provided with a pump element (13) on its inlet side, and the sliding contact surface between the eccentric shaft portion (5a) and the piston (9), that is, the cylinder chamber.
An intermediate outlet is opened in (6a), and the pump element (1
Lubricating oil pumped up from the bottom oil sump (2a) in 3) is supplied to the oil supply channel (10).
The gas is supplied from the intermediate outlet to the inside of the cylinder chamber (6a).

Further, the cylinder (6) is provided with a suction port (21) opening to the outer peripheral wall of the cylinder chamber (6a), and the suction port (21) sucks from the outside of the closed casing (2). Tube (2
b) is connected. In addition, as shown in FIG. 3, the front head (7) and the rear head (8) have circular discharge ports that are opened on both upper and lower walls of the cylinder chamber (6a).
(22), (22) are provided, and each discharge port (22) has a cylinder chamber
(6a) A discharge valve (23) is provided which opens when the pressure in the high pressure chamber (35, which will be described later in detail) reaches or exceeds a predetermined value.
Each discharge valve (23) is a valve body (23a) that opens and closes the discharge port (22).
And a valve retainer (23b) for restricting the opening of the valve body (23a) by a contact amount or more. A fluid such as a refrigerant gas discharged from the discharge port (22) of the rear head (8) passes through the cylinder (6) and both heads (7) and (8) in the axial direction (not shown). ) Through the front head
The fluid is discharged from the discharge port (22) of (7) to the outside of the closed casing (2). Further, the cylinder (6) is formed with a cylindrical bush hole (24) (hole) penetrating in the axial direction at a position between the suction port (21) and the discharge port (22). The part (24) has an opening (24a) that opens to face the cylinder chamber (6a) in a part of the circumference.

The piston (9) is integrally provided with a blade (31) extending radially from the outer peripheral surface (12) of the piston (9). The blade (31) is integrally formed with the piston (9), or is made of a separate member and is formed by connecting the two with a concavo-convex fitting structure or an adhesive or the like. The protruding tip side of the blade (31) is inserted into the bush hole (24), while the axial center (O
Swing bush (32) with a roughly cylindrical shape that swings around (B) as a fulcrum
Is swingably inserted. The swinging bush (32) is formed with a receiving groove (33) for receiving the protruding tip side of the blade (31) through the opening (24a) so as to be movable back and forth. The swing bush (32) allows the protruding tip side of the blade (31) to move forward and backward while the blade (31) is sandwiched in the receiving groove (33) and is integral with the blade (31). Is provided so as to swing in the bush hole (24). The blade (31) is a cylinder chamber between the inner peripheral wall (11) of the cylinder (6) and the outer peripheral surface (12) of the piston (9).
(6a) is divided into a low pressure chamber (34) leading to the suction port (21) and a high pressure chamber (35) leading to the discharge port (22).
(9) revolves along the inner peripheral wall (11) of the cylinder chamber (6a) so that it swings around the swing bush (32) via the blade (31), and the suction port (21 ) Is compressed and discharged from the discharge port (22).
Incidentally, (2c) in FIG. 4 is an external discharge pipe connected to the upper part of the closed casing (2).

Further, as a characteristic part of the present invention, the piston (9) is arranged with respect to the axis (OH) of the eccentric shaft (5a) so as to enlarge the bore cross-sectional area of the cylinder chamber (6a). The piston shaft (OP) is eccentrically arranged on the opposite side of the blade (31). Further, as shown in FIG. 2, the eccentric shaft portion (5a) has an axial center (OH) and a piston shaft (OP)
(9) is provided on the reciprocating movement axis (m) of the blade (31) passing through the axial center (OB) of the bush hole (24) when revolving,
When the piston (9) revolves, the shaft center (OH) of the eccentric shaft (5a) swings around the shaft center (OK) of the drive shaft (5) in a perfect circular locus (Y). On the other hand, the swing locus (X) of the piston axis (OP)
Is the distance between the shaft center (OH) of the eccentric shaft part (5a) and the piston shaft (OP) on the forward / backward moving axis (m) of the blade (31).
Since (a) is invariant, the eccentric shaft (5a) axis (O
The point data values (indicated by black circles in Fig. 2) of the piston axis (OP) on the advancing / retreating movement axis (m) with respect to the swing locus (Y) of (H) are sequentially obtained by the contour line drawn.

On the other hand, the axis center (OC) of the cylinder chamber (6a) is
In order to revolve the outer peripheral surface (12) of the piston (9) along the inner peripheral wall (11) of the cylinder chamber (6a) along with the swing locus (X) of the piston shaft (OP), the drive shaft ( It is eccentric to the opposite side of the blade (31) with respect to the axis (OK) of 5). Shaft center (OC) of the cylinder chamber (6a) and shaft center (OK) of the drive shaft (5)
Are provided on the forward / backward movement axis (m) of the blade (31) at the top dead center position or the bottom dead center position of the piston (9), respectively. And the outer peripheral surface (12) of the piston (9)
Is formed in a circular cross-section centered on the piston shaft (OP), while the inner peripheral wall (11) of the cylinder chamber (6a)
Attaches the outer peripheral surface (12) of the piston (9) to the piston shaft (O
It is formed in a non-circular cross-section whose diameter is enlarged on the low-pressure rotation region side and the high-pressure rotation region side, respectively, so as to revolve along the envelope linear swing locus (X) of P). in this case,
The eccentric shaft (5a) shaft center (OH), drive shaft (5) shaft center (OK), piston shaft (OP) and cylinder chamber (6a) shaft center (OC) are shown in Fig. 9) The blades (31) at the top dead center position are arranged side by side on the advancing / retreating movement axis (m) from the blade (31) side, of which the axis (OH) of the eccentric shaft (5a) and the cylinder chamber The axis (6a) (OC) is substantially concentric with the forward / backward movement axis (m) of the blade (31) at the bottom dead center position of the piston (9) shown in FIG.

Therefore, in the above embodiment, the piston shaft (OP) moves the blade (31) forward and backward with respect to the eccentric shaft portion (5a) without changing the shaft center (OH). Axis of movement
(m) is provided eccentrically on the opposite side to the blade (31), while the axis (OC) of the cylinder chamber (6a) is on the swing locus (X) of the piston axis (OP). As the piston (9) revolves with respect to the axis (OK) of the drive shaft (5), the forward / backward movement axis
It is eccentrically provided on the side opposite to the blade (31) on (m). As a result, the diameter of the piston (9) is expanded by using the eccentric shaft (5a) as it is, and the bore diameter of the cylinder chamber (6a) is maximized on the side opposite to the blade (31). The bore cross-sectional area is enlarged without being restricted by the bush hole (24) in the inner peripheral portion of the cylinder (6), and the bore volume of the cylinder chamber (6a) is effectively increased.

Therefore, it is possible to secure the bore volume of the cylinder chamber (6a) even if the cylinder height is made small, and by minimizing the cylinder height, the cylinder chamber (6a)
The fluid leakage gap between the inner peripheral wall (11) of the cylinder and the outer peripheral surface (12) of the piston (9) can be reduced in the direction of the piston axis (OP), and the inner peripheral wall (11) of the cylinder chamber (6a) can be reduced. And the piston shaft (O) during machining such as polishing the outer peripheral surface (12) of the piston (9).
The bending of a processing tool such as an end mill that is inserted in the P direction is suppressed, the processing accuracy of the processing tool can be improved, and the swing compressor (1) can be made highly efficient. In addition, the cylinder chamber (6
By increasing the bore diameter of a), it is possible to minimize the eccentricity of the eccentric shaft part (5a) with respect to the shaft center (OK) of the drive shaft (5), and the blade (31) shrinks in the forward and backward direction. Being a Blade (31)
It is possible to achieve cost reduction by shortening the processing size of. As a result, cylinder height and eccentric shaft (5a)
The design of the compression element (4) can be optimized by minimizing the amount of eccentricity.

Further, since the outer peripheral surface (12) of the piston (9) is formed in a circular cross section and the inner peripheral wall (11) of the cylinder chamber (6a) is formed in a non-circular cross section, for example, the piston
Cylinders with a non-round cross section by swinging a tool with a round cross section of the same shape as (9) along the envelope line trajectory (X) with the piston axis (OP) as the fulcrum. Inner wall of chamber (6a) (1
The processing of 1) can be easily performed.

Next, a modified example of this embodiment will be described.

First, as a first modification, as shown by the alternate long and short dash line in FIG. 1, the inner peripheral wall (11 ') of the cylinder chamber (6a) is centered on the axial center (OC) of the cylinder chamber (6a). While the outer peripheral surface (12 ') of the piston (9) is formed to have a perfect circular cross-section, the cylinder chamber (6) is moved along with the swing locus (X) of the piston shaft (OP).
The piston is revolved around the inner wall (11 ') of a).
(9) The blade at the top dead center position or the bottom dead center position (3
The cross section is formed in a non-round shape with a diameter enlarged in the direction of the forward / backward movement axis (m) in 1). In this case, since the inner peripheral wall (11 ') of the cylinder chamber (6a) has a perfect circular cross-section that is easy to machine, machining on the inner peripheral wall (11') side, which is restricted during machining, can be done with a machining tool such as an end mill. Can be performed easily and accurately. On the other hand, pistons that are not restricted during processing
Since the outer peripheral surface (12 ') side of (9) has a non-circular cross section, the outer peripheral surface (12') can be accurately and easily processed into a non-round cross section.

As a second modification, as shown by the chain double-dashed line in FIG. 1, the outer peripheral surface (12 '') of the piston (9) and the inner peripheral wall (11 '') of the cylinder chamber (6a) are Inner peripheral wall of cylinder chamber (6a)
In order to revolve the outer peripheral surface (12 '') of the piston (9) with respect to (11 '') along the swing locus (X) of the piston shaft (OP), the low pressure rotation area side and the high pressure rotation area side, respectively. The cross-section is formed to have a non-round shape with the diameter enlarged toward the side. In this case, in the cylinder chamber (6
The unnecessary wall thickness between the inner peripheral wall (11 '') of a) and the outer peripheral wall of the cylinder (6) is used efficiently, and the bore diameter of the cylinder chamber (6a) is efficiently expanded to increase the bore volume. It can be expanded more effectively.

The present invention is not limited to the above-described embodiment and each modified example, but includes various modified examples. For example, in the above-described embodiment, the piston axis (OP) is provided on the advancing / retreating movement axis (m) of the blade (31), but at the position where the piston axis deviates from the advancing / retreating movement axis of the blade, the blade is It may be provided so as to be eccentric on the opposite side, and in this case as well, the bore diameter of the cylinder chamber is expanded and the bore volume is expanded.

Further, in the above embodiment, the eccentric shaft portion (5a)
The shaft center (OH) of the drive shaft (5) is eccentric to the shaft center (OK) of the cylinder chamber (6a) with the same amount of eccentricity as the shaft center (OC) of the drive shaft (5). On the other hand, it may be eccentric with an eccentric amount different from the axial center of the cylinder chamber.

[0032]

As described above, according to the swing compressor of the invention described in claim 1, the piston shaft is eccentric to the side opposite to the blade with respect to the shaft center of the eccentric shaft portion, while the shaft center of the cylinder chamber is provided. Is eccentric to the side opposite to the blade with respect to the axis of the drive shaft, effectively increasing the bore volume of the cylinder chamber, effectively reducing the cylinder height to reduce the fluid leakage gap, and The efficiency of the swing compressor can be improved by improving the machining accuracy, and the blade cost can be reduced by reducing the blade by minimizing the eccentricity of the eccentric shaft portion. Therefore, the cylinder height and the eccentric shaft can be reduced. It is possible to optimize the design of the compression element by minimizing the eccentricity of the portion.

According to the swing compressor of the second aspect of the invention, since the piston shaft is provided on the advancing / retreating movement axis of the blade, the bore diameter of the cylinder chamber is maximized to increase the bore cross-sectional area. The bore volume of the cylinder chamber can be expanded more effectively.

According to the swing compressor of the third aspect of the invention, since the outer peripheral surface of the piston is formed to have a perfect circular cross section and the inner peripheral surface of the cylinder chamber is formed to have a non-perfect circular cross section, the same shape as the piston is formed. The inner peripheral surface of the cylinder chamber can be easily processed by the processing tool or the like.

According to the swing compressor of the fourth aspect of the present invention, the inner peripheral surface of the cylinder chamber is formed in a perfect circular cross section, and the outer peripheral surface of the piston is formed in a non-perfect circular cross section. Therefore, the inner peripheral surface of the cylinder chamber and the outer peripheral surface of the piston can be machined accurately and easily.

Further, according to the swing compressor of the fifth aspect of the present invention, since the outer peripheral surface of the piston and the inner peripheral surface of the cylinder chamber are both formed to have a non-round shape in cross section, unnecessary thickness in the radial direction of the cylinder is eliminated. The bore diameter of the cylinder chamber can be efficiently expanded by efficiently utilizing the thickness, and the bore volume can be expanded more effectively.

[Brief description of the drawings]

FIG. 1 is a cross-sectional plan view of a compression element at a bottom dead center position of a piston cut near an eccentric shaft portion according to an embodiment of the present invention.

FIG. 2 is an explanatory diagram illustrating a swing locus of a piston shaft with respect to an axis of an eccentric shaft portion when the piston revolves.

FIG. 3 is a vertical sectional front view of the compression element cut near the discharge port.

FIG. 4 is a vertical sectional side view of the swing compressor.

[Explanation of symbols]

 (1) Swing compressor (5) Drive shaft (5a) Eccentric shaft (6) Cylinder (6a) Cylinder chamber (9) Piston (11), (11 '), (11' ') Cylinder chamber inner wall ( (Inner surface) (12), (12 '), (12' ') Piston outer surface (21) Suction port (22) Discharge port (24) Bush hole (hole) (24a) Opening (31) Blade ( 32) Oscillating bush (34) Low pressure chamber (35) High pressure chamber (m) Forward / backward movement axis (axis) (OB) Bush hole axis (OC) Cylinder chamber axis (OH) Eccentric axis axis ( OK) Drive shaft axis (OP) Piston shaft (X) Piston shaft swing locus

Front page continuation (72) Kenichi Saito, 1304 Kanaoka-cho, Sakai City, Osaka Prefecture Daikin Industries, Ltd.Kanaoka Factory, Sakai Manufacturing Co., Ltd. (72) Go, Fukunaga 1304, Kanaoka-machi, Sakai City, Osaka Daikin Industries, Inc. In the factory (72) Inventor Katsumi Kato 1304 Kanaoka-cho, Sakai City, Osaka Daikin Industries, Ltd.Sakai Plant Kanaoka Factory (72) Inventor Katsumi Kawahara 1304, Kanaoka-machi, Sakai City, Osaka Daikin Industries Ltd. (72) Inventor Takeyoshi Okawa 1304 Kanaoka-machi, Sakai City, Osaka Prefecture Daikin Industries, Ltd. Sakai Factory Kanaoka Factory

Claims (5)

[Claims] 1. A cylinder (6) having a cylinder chamber (6a) in which an intake port (21) and a discharge port (22) are open, and a cylinder (6a) disposed in the cylinder chamber (6a), the inner peripheral portion of which is a drive shaft. (Five)
Piston (9) rotatably fitted to the eccentric shaft (5a) of
And a low pressure chamber (34) and a discharge port (2) which are connected to the outer periphery of the piston (9) in a protruding manner and communicate the cylinder chamber (6a) with the suction port (21).
It is provided between the blade (31) that divides the high pressure chamber (35) communicating with 2) and the suction port (21) and discharge port (22) of the cylinder (6), and the cylinder chamber (6a) A hole (24) having an opening (24a) to be opened, and a shaft (OB) extending in the piston axis (OP) direction in the hole (24) are provided so as to be swingable, and the blade (31) Swing bush (32) that supports the protruding tip side so that it can swing and move back and forth.
In the swing compressor (1), which is configured so that the piston (9) revolves in the cylinder chamber (6a) with the rotation of the drive shaft (5), the piston (9) is To increase the bore cross-sectional area of the cylinder chamber (6a), eccentric the piston shaft (OP) to the opposite side of the blade (31) with respect to the shaft center (OH) of the eccentric shaft portion (5a). The piston shaft (OP) is provided on the piston (9)
Of the eccentric shaft part (5a) that swings in a substantially circular shape around the shaft center (OK) of the drive shaft (5) when revolving , And the shaft center (OC) of the cylinder chamber (6a) is the same as the piston shaft (12), (12 '), (12''). With the swing locus (X) of (OP), the inner peripheral surface (11), (11 '), (1
A swing compressor characterized by being eccentric to the side opposite to the blade (31) with respect to the axis (OK) of the drive shaft (5) so as to revolve along 1 ''). 2. The piston shaft (OP) is connected to the blade (3).
On the axis (m) extending in the forward / backward movement direction of 1) above the blade (3
The swing compressor according to claim 1, wherein the swing compressor is eccentrically provided on the side opposite to (1). 3. The outer peripheral surface (12) of the piston (9) is formed in a perfect circular cross-section around the piston shaft (OP), while the inner peripheral surface (12) of the cylinder chamber (6a) is formed. 11) is the piston (9) above
The swing compressor according to claim 1 or 2, wherein the outer peripheral surface (12) is formed in a non-circular cross-section so as to revolve along the swing locus (X) of the piston shaft (OP). 4. The inner peripheral surface (11 ′) of the cylinder chamber (6a) is
On the other hand, the outer peripheral surface (12 ') of the piston (9) is formed so as to have a perfect circular shape centered on the axial center (OC) of the cylinder chamber (6a).
Along with the swing locus (X) of (P), the inner peripheral surface (1
The swing compressor according to claim 1 or 2, which is formed to have a non-circular cross-section that revolves along 1 '). 5. The outer peripheral surface (12 '') of the piston (9) and the inner peripheral surface (11 '') of the cylinder chamber (6a) are provided in the cylinder chamber (6).
a) inner surface (11 '') against piston (9) outer surface (12 '')
The swing compressor according to claim 1 or 2, wherein each of the swing compressors is formed to have a non-circular cross section so as to revolve along the swing locus (X) of the piston shaft (OP).