JPH1047278A - Swing compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To stabilize behavior of a piston by forming a tip part of a blade in a taper shape so that a dimension in the direction of its swinging axis becomes small toward the tip side of the blade in a swing compressor having a piston formed by integrally arranging the blade on a roller. SOLUTION: In a compressing mechanism part containing a piston 4 where a blade 6 is arranged on a roller 5, a tip part of the blade 6 is formed in a taper shape so that a dimension in the direction of its winging axis P becomes small toward the tip side. That is, taper parts 6h are arranged on upper and lower both surfaces of the tip part of the blade 6, and these taper parts 6h are arranged in a tip side position from a part of the blade 6 positioned in a holding bush 7 when the piston 4 is positioned in the lower dead center. Therefore, when the blade 6 moves in the direction for advancing to the holding bush 7, it is put in a condition where lubricating oil enters between the taper parts 6h and a cylinder 1 or the holding bush 7, and oil film forming capacity between both is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a swing compressor (kinney type compressor) having a piston in which a blade is integrally provided with a revolving roller, and more particularly to a measure for stabilizing the behavior of the piston.

[0002]

2. Description of the Related Art This type of compressor is disclosed in, for example,
As shown in FIG. 6 and FIG. 7, as shown in FIGS. 6 and 7, a suction port (b) and a discharge port (c) are opened in a cylinder chamber (a) having a circular cross section in a circumferential direction. Cylinder (A) and a crank that is rotatably provided around an axis (P) through the cylinder (A) and has an eccentric shaft (d) in a cylinder chamber (a). The crankshaft (B) is rotatably externally fitted to the shaft (B) and the eccentric shaft portion (d) of the crankshaft (B), and revolves around the shaft (P) by rotation of the crankshaft (B). A roller (e) is provided with a piston (C) integrally provided with a blade (f) having a rectangular cross section so as to protrude outward in the radial direction, and a cylinder chamber (a) of the cylinder (A). It is arranged at a position between the suction port (b) and the discharge port (c) facing it, and the blade ( ) So as to be able to swing around an axis (Q) parallel to the axis (P) of the crankshaft (B) and to be reciprocally movable in the length direction of the blade (f). A bush (D). The low pressure chamber (g) in the cylinder chamber (a) defined by the blade (f) and facing the suction port (b) is operated from the suction port (b) with the revolving motion of the roller (e). The working fluid in the high pressure chamber (h) in the cylinder chamber (a) defined by the blade (f) and facing the discharge port (c) is discharged from the discharge port (c) while the fluid is sucked. ing.

[0003] In the swing compressor configured as described above, unlike the rolling piston type compressor in which the roller and the blade are separate bodies, there is no relative movement between the roller (e) and the blade (f). It is said that friction loss and power loss can be reduced by that much.

[0004]

In the above-mentioned swing compressor, the piston (C) having the roller (e) and the blade (f) integrated with each other is used. In terms of point, there is a drawback that it is smaller than a rolling piston type compressor.

More specifically, the blade (f) reciprocates with respect to the holding bush (D). When the moving direction is switched, the moving speed becomes zero. In addition to the small capacity, the edge of the tip of the blade (f) is easily squeezed with the cylinder (A) or the holding bush (D) when moving in the advance direction with respect to the holding bush (D).
There is a problem that the behavior of the device tends to be unstable.

Further, since it is necessary to match the axial dimension of the roller (e) with the axial dimension of the blade (f), it is difficult to obtain the accuracy of the axial dimension of the piston (C) itself. There is also a problem that it is more difficult to reduce the axial gap between the cylinder (A) and the piston (C) which greatly affects the efficiency of the compressor than in the case of the rolling piston type.

SUMMARY OF THE INVENTION The present invention has been made in view of the above points, and a main object of the present invention is to provide a swing compressor having a piston in which a revolving roller is integrally provided with a blade. It is an object of the present invention to stabilize the behavior of the piston irrespective of the reciprocating motion of the blade by modifying the shape of the piston.

[0008]

In order to achieve the above object, according to the present invention, the tip of the blade is provided in a tapered shape, the oil film forming ability is improved by a wedge effect in the tapered portion, and the blade is moved in the forward direction. Prevention of prying when moving starts, thereby stabilizing the behavior of the piston.

Specifically, according to the first aspect of the present invention, as shown in FIGS. 2 and 3, a suction port (1a) and a discharge port (1b) are provided in a cylinder chamber (2) having a circular cross section in a circumferential direction. A cylinder (1) which is opened at an offset and is provided rotatably about an axis (P) in a state penetrating the cylinder (1), and an eccentric shaft (3a) is provided in a cylinder chamber (2). )
A crankshaft (3) having an outer periphery rotatably fitted to an eccentric shaft portion (3a) of the crankshaft (3), and revolving around the shaft center (P) by rotation of the crankshaft (3). A piston (4) having a blade (6) having a rectangular cross-section protruding outward in the radial direction and a cylinder (1);
The blade (6) is disposed at a position between the suction port (1a) and the discharge port (1b) facing the cylinder chamber (2), and the blade (6) is parallel to the axis (P) of the crankshaft (3). (Q) and a holder (7) for holding the blade (6) reciprocally in the length direction of the blade (6),
With the revolution of the roller (5), the suction port (1a) is partitioned by the blade (6) into the low-pressure chamber (2a) in the cylinder chamber (2) facing the suction port (1a).
The working fluid is sucked from the cylinder chamber (2), while the cylinder chamber (2) is partitioned by the blade (6) and faces the discharge port (1b).
It is assumed that a working fluid is discharged from the discharge port (1b) of the working fluid in the high-pressure chamber (2b).

Then, the tip of the blade (6) is
As shown in FIG. 1, the blade (6) is formed in a tapered shape such that its dimension in the direction of the pivot axis (Q) (the dimension in the vertical direction in the figure) decreases toward the tip end side of the blade (6). .

In the above construction, as the piston (4) moves from the bottom dead center toward the top dead center due to the rotation of the crankshaft (3), the tip of the blade (6) is moved to the holder (7). When moving in the direction (right direction in FIG. 1), the tapered portions (6h) and (6h) of the blade (6)
Since the lubricating oil enters the wedge shape between the cylinder (1) and the holder (7), the ability to form an oil film between the two is improved. In addition, the edge caused by the edge of the tip of the blade (6) with respect to the cylinder (1) or the holder (7) hardly occurs due to the absence of such an edge. Thus, the behavior of the piston (4) is stabilized.

Furthermore, in the direction (horizontal direction in FIG. 1) of extension of the blade (6), the piston dimensions are the tapered portion of the end surface shape of the (4) dimensions (6h) (L ₀ -L ₁₎
Therefore, the accuracy of the piston (4) in the axial direction can be easily obtained.

According to a second aspect of the present invention, in the first aspect of the present invention, when the piston (4) is located at the bottom dead center, a portion of the blade (6) positioned in the holder (7) is located on the tip side. The portion was formed in a tapered shape.

In the above arrangement, when the piston (4) reaches the bottom dead center, each tapered portion (6) of the blade (6)
h) and (6h) are located inside the holder (7),
It does not move to the position facing the cylinder chamber (2). Therefore, leakage of the working fluid due to the communication between the low-pressure chamber (2a) and the high-pressure chamber (2b) through the tapered portions (6h) and (6h) is avoided.

According to the third aspect of the invention, on the same premise as in the first aspect of the invention, as shown in FIG. 5, the blade (6) is moved when the piston (4) is located at the bottom dead center. The tip of the blade (6) is provided so as to be positioned inside the holder (7). Then, the blade (6)
Of the tip of the blade (6) in the direction perpendicular to each of the direction of its pivot axis (Q) and the length of the blade (6) (the dimension in the left-right direction in the figure). It was formed in a tapered shape that became smaller toward the side.

In the above configuration, when the piston (4) is located at the bottom dead center, the tip of the blade (6) is positioned inside the holding body (7). When the piston reaches the top dead center, the amount by which the blade (6) protrudes from the holder (7) is adjusted so that the tip of the blade protrudes from the holder when the piston is located at the bottom dead center. Less than in the conventional case. Therefore, the space for receiving the tip of the blade (6) protruding from the holder (7) can be reduced, and the diameter of the swing compressor can be reduced accordingly.

Further, as the piston (4) moves from the bottom dead center toward the top dead center by the rotation of the crankshaft (3), the tip of the blade (6) advances to the holder (7). When the blade (6) moves in the direction in which the blade (6) moves in the direction perpendicular to the direction of the pivot axis (Q) and the length direction of the blade (6), Since it has a tapered shape that gradually decreases, lubricating oil enters a wedge shape between the tapered portions (6w) and (6w) at the tip of the blade (6) and the holding body (7). The ability to form an oil film between the layers is improved. Further, the prying of the tip of the blade (6) with respect to the holding body (7) hardly occurs. Therefore, also in the present invention, the behavior of the piston (4) is stabilized.

According to a fourth aspect of the present invention, in the third aspect of the present invention, when the piston (4) is located at the bottom dead center, the piston (4) is positioned at the position of the pivot axis (Q) in the holding body (7). A portion closer to the tip than the blade (6) is formed in a tapered shape.

In the above configuration, when the piston (4) reaches the bottom dead center, each tapered portion (6) of the blade (6)
w) and (6w) are located on the distal end side of the position of the swing axis (Q). Accordingly, when the tip of the blade (6) moves in a direction to advance in the holder (7) as the piston (4) moves from the bottom dead center toward the top dead center, the taper is reduced. Unnecessary rotation of the holder (7) is restricted as compared with the case where the portion is located closer to the base portion than the position of the pivot axis (Q). Accordingly, the guide of the swinging motion of the blade (6) by the holding body (7) is properly performed, despite the fact that the blade (6) is provided with the tapered portions (6w) and (6w).

[0020]

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

(Embodiment 1) FIG. 2 shows the overall configuration of a swing compressor according to Embodiment 1 of the present invention. This compressor is used to compress refrigerant gas in a refrigerant circuit of an air conditioner. Used.

The swing compressor has a cylindrical closed casing (11) arranged in the vertical direction. A suction pipe (11) for introducing refrigerant gas into the casing (11) is provided on a lower side wall of the casing (11).
a) is provided so as to protrude toward the side (the right side in the figure). Although not shown, the suction pipe (11a) is connected to an evaporator of the refrigerant circuit. On the other hand, the upper end wall of the casing (11) has a discharge pipe (11) for discharging the high-pressure refrigerant gas in the casing (11) to the outside.
b) is provided so as to protrude upward.
This discharge pipe (11b) is connected to a condenser (not shown).

A compression mechanism (1) for sucking, compressing and discharging the refrigerant gas is provided below the casing (11).
2), and a drive mechanism (13) for operating the compression mechanism (12) are arranged on the upper side, respectively. Further, a primary space (14) for storing the refrigerant gas discharged from the compression mechanism (12) is provided between the compression mechanism (12) and the drive mechanism (13). In addition, above the driving mechanism (13),
2 for storing the refrigerant gas discharged from the primary space (14) through the clearance space of the drive mechanism (13).
A next space (15) is provided. On the other hand, below the compression mechanism (12), it is returned from the primary space (14) and the compression mechanism (12) and the drive mechanism (13).
An oil sump (17) for accumulating the lubricating oil supplied to each sliding portion is provided.

As shown in FIG. 3, the compression mechanism (12) has a suction port (1) in a cylinder chamber (2) having a circular cross section.
a) and a cylinder (1) in which the discharge port (1b) is opened while being shifted in the circumferential direction, and provided so as to be rotatable around an axis (P) while penetrating the cylinder (1) in the vertical direction. A crankshaft (3) having an eccentric shaft (3a) in a cylinder chamber (2); and a crankshaft (3) externally fitted to the eccentric shaft (3a) of the crankshaft (3). ), A piston (5) integrally provided with a roller (5) that revolves around the axis (P) so as to protrude outward in the radial direction with a blade (6) having a rectangular cross section. 4) and the suction port (1a) and the discharge port (1b) facing the cylinder chamber (2) of the cylinder (1). The blade (6) is connected to the axis of the crankshaft (3). The blade (6) swingable about an axis (Q) parallel to the center (P); And a holding bushing as a substantially cylindrical holder for holding and reciprocating (7) in the longitudinal direction. And, with the revolving motion of the roller (5),
The blade (6) is partitioned and the suction port (1
The refrigerant gas is sucked from the suction port (1a) into the low-pressure chamber (2a) in the cylinder chamber (2) facing the a), while the cylinder chamber (6) is partitioned by the blade (6) and faces the discharge port (1b). The refrigerant gas in the high pressure chamber (2b) in 2) is discharged from the discharge port (1b).

Specifically, the cylinder (1) is fixed to the inner peripheral wall surface of the closed casing (11) and has a vertically open cylinder block (20), and an upper surface of the cylinder block (20). The front head (21) is hermetically joined and the rear head (22) is hermetically joined to the lower surface of the cylinder block (20). The front head (21), the cylinder block (20) and the rear head (22) are integrally fastened by a plurality of bolts (23). At the center of the front head (21), a cylindrical front bearing (21a) is provided so as to protrude toward the primary space (14). On the other hand, a cylindrical rear bearing (22a) is provided at the center of the rear head (22).
It is provided so as to protrude toward 7). The crankshaft (3) is rotatably supported by the bearings (21a) and (22a).

The suction port (1a) and the discharge port (1b) are open to the cylinder chamber (2) at positions close to each other, and a suction port from the suction pipe (11a) to the suction port (1a) is It is provided so as to penetrate the cylinder block (20) in the radial direction. On the other hand, a discharge hole communicating from the discharge port (1b) to the external space of the cylinder (1) is provided so as to penetrate the front head (21), and a discharge valve disposed on the upper surface of the front head (21). (2
4) prevents the backflow of the refrigerant gas. A muffler member (25) is mounted on the front head (21) with an annular gap between the muffler member and the front bearing (21a).

A substantially cylindrical hole (20a) extending in the direction of the pivot axis (Q) of the blade (6) is provided at a portion between the suction port (1a) and the discharge port (1b) of the cylinder block (20). ) Is provided in communication with the cylinder chamber (2), and the holding bush (7) is disposed in the hole (20a) so as to be rotatable around the pivot axis (Q). The holding bush (7) includes a pair of holding members (7a) and (7a) each having a substantially semicircular cross section, and is formed between the holding members (7a) and (7a). The blade (6) is inserted through the slot (7b). On the side of the hole (20a) accommodating the holding bush (7) opposite to the cylinder chamber (2), a blade (6) penetrating the slot portion (7b) radially outward. Space part (20b) for receiving the tip part in a swingable manner
Is provided.

The roller (5) has a cylindrical shape whose upper and lower ends are open. As shown in FIG. 3, the position of the top dead center which closes the suction port (1a) and the discharge port (1b) during the revolving motion. Is assumed to have a revolution angle of 0 °, the volume of the low-pressure chamber (2a) becomes the minimum while the volume of the high-pressure chamber (2b) becomes the maximum. Further, at the position of the bottom dead center where the revolving angle is 180 ° (the position shown in FIG. 1), the low-pressure chamber (2
The volumes of a) and the high pressure chamber (2b) are equal to each other.

On the other hand, the drive mechanism (13) is provided with a stator (1) fixed to the inner peripheral wall surface of the closed casing (11).
3a) and an electric motor having a rotor (13b) arranged on the inner peripheral side of the stator (13a), and fitted with the upper half of the crankshaft (3) and integrally connected to rotate. I have. A gap space is formed between the inner peripheral surface of the stator (13a) and the outer peripheral surface of the rotor (13b) to connect the primary space (14) and the secondary space (15) to each other.

In the oil reservoir (17), the lower end of the crankshaft (3) is immersed in a predetermined amount of lubricating oil stored in the oil reservoir (17). A centrifugal oil pump (26) is provided at the lower end, and an oil sump (17) is provided according to the rotation of the crankshaft (3).
Lubricating oil is sucked into the crankshaft (3). Further, an oil passage (27) is provided inside the crankshaft (3) along the axis (P) thereof, and the sucked lubricating oil is supplied to the compression mechanism (12) and the drive mechanism (13). ) Is supplied to each sliding portion.
Therefore, in the compression mechanism section (12), the refrigerant gas is compressed in a state of a mixed fluid in which the lubricating oil is mixed with the refrigerant gas and discharged to the primary space (14). An oil return hole (28) for returning the lubricating oil separated from the refrigerant gas in the primary space (14) to the oil reservoir (17) is provided around the compression mechanism (12). .

In this embodiment, the tip of the blade (6) of the piston (4) in the compression mechanism (12) is, as shown in an enlarged view in FIG.
Is formed in a tapered shape in which the dimension in the direction of the pivot axis (P) (the dimension in the vertical direction in the figure) decreases toward the tip end (the right end side in the figure). That is, tapered portions (6h) and (6h) are formed on both upper and lower surfaces of the tip of the blade (6).
Is provided. In addition, each of these tapered portions (6h)
Is a position on the tip side from the portion of the blade (6) positioned in the holding bush (7) when the piston (4) is located at the bottom dead center (the point where the revolving angle of the roller (5) becomes 180 °). Are located in

Here, the operation of the compression mechanism (12) of the swing compressor will be described. As the piston (4) moves from the bottom dead center toward the top dead center due to the rotation of the crankshaft (3), when the blade (6) moves in the direction to advance to the holding bush (7), Since the tip of the blade (6) has a tapered shape in which the dimension in the direction of the pivot axis (Q) decreases toward the tip, the tip of the blade (6) is schematically shown in FIG. The lubricating oil enters a wedge shape between the tapered portions (6h), (6h) and the cylinder (1) or the holding bush (7), thereby improving the oil film forming ability between the two. In addition, the edge caused by the edge of the tip of the blade (6) with respect to the cylinder (1) or the holding bush (7) is unlikely to occur due to the absence of such an edge. Thus, the behavior of the piston (4) is stabilized.

Therefore, according to the present embodiment, in the swing compressor provided with the piston (4) in which the roller (5) is integrally provided with the blade (6), the upper and lower surfaces of the tip of the blade (6) are provided. (6h), (6h)
Provided, the blade (6) reciprocates with respect to the holding bush (7) with the swinging movement of the piston (4). The ability to form an oil film between the bush (7) and the cylinder (1) can be improved, and at the same time, it is possible to reduce the occurrence of bulging due to the edge of the tip of the blade (6). The behavior of 4) can be stabilized.

Furthermore, the dimensions of the piston (4) the end face in the direction of extension of the blade (6), as shown in FIG. 1, the minute of the tapered portion (6h) (L ₀ -L ₁₎ be as short as Therefore, it is possible to easily obtain the accuracy in the axial direction of the piston (4).
In addition, the axial clearance between the pistons (4) can be reduced to increase the compressor efficiency.

(Embodiment 2) FIG. 5 shows a main part of a swing compressor according to Embodiment 2 of the present invention. The same parts as those in the first embodiment are denoted by the same reference numerals.

In this embodiment, the compression mechanism (1)
The blade (6) of the piston (4) in 2) is shown in FIG.
As shown by a solid line, when the piston (4) is located at the bottom dead center, the tip of the blade (6) is provided so as to be positioned inside the holding bush (7).
That is, the length of the blade (6) is shorter than in the conventional case. Then, the tip of the blade (6) has a dimension in a direction perpendicular to each of the direction of the pivot axis (Q) and the length direction of the blade (6) (the dimension in the left-right direction in FIG. ) Are formed in a tapered shape that becomes smaller toward the tip end side of the blade (6). That is, tapered portions (6) are provided on both left and right surfaces of the tip of the blade (6).
w) and (6w) are provided. Further, each tapered portion (6w) is larger than the portion of the blade (6) positioned at the position of the swing axis (Q) in the holding bush (7) when the piston (4) is located at the bottom dead center. It is arranged at a position on the distal end side (upper end side in the figure). The other parts are the same as those in the first embodiment, and the description is omitted.

Next, the operation of the compression mechanism (12) of the swing compressor configured as described above will be described. As the piston (4) moves from the bottom dead center toward the top dead center due to the rotation of the crankshaft (3), when the blade (6) moves in the direction to advance to the holding bush (7), The tip of the blade (6) has a tapered shape in which the dimension in the direction perpendicular to each of the direction of the pivot axis (Q) and the length of the blade (6) decreases toward the tip. The tapered portion (6) of the blade (6)
w), (6w) and the holding bush (7) are in a state in which the lubricating oil enters the wedge shape, thereby improving the oil film forming ability between the two. At this time, the tip of the blade (6) is hardly prying the holding bush (7). Therefore, also in the present embodiment, the piston (4)
Is stabilized.

When the piston (4) is located at the bottom dead center, the tip of the blade (6) is positioned inside the holding bush (7). The piston (4)
When the piston reaches the top dead center, the amount of the blade (6) projecting from the holding bush (7) is set so that the tip of the blade projects from the holding bush when the piston is located at the bottom dead center. Less than in the conventional case. Therefore, the space (20b) for receiving the tip of the blade (6) protruding from the holding bush (7) can be small, and the diameter of the swing compressor can be reduced accordingly.

When the piston (4) reaches the bottom dead center, each tapered portion (6w), (6w) of the blade (6)
w) is located on the distal end side with respect to the position of the swing axis (Q). Accordingly, when the blade (6) moves in a direction to advance to the holding bush (7) with the movement of the piston (4) from the bottom dead center toward the top dead center, the respective tapered portions (6w) are moved. Unnecessary rotation of the holding bush (7) is restricted as compared with the case where (2) is located closer to the base side than the position of the swing axis (Q). Therefore, the tapered portion (6
Despite the provision of (w) and (6w), the swinging movement of the blade (6) by the holding bush (7) is properly performed.

Therefore, according to the present embodiment, it is possible to prevent the tip of the blade (6) from being twisted with respect to the holding bush (7), and to improve the oil film forming ability between the two. In addition to stabilizing the behavior of 4), the amount by which the tip of the blade (6) projects through the holding bush (7) when the piston (4) reaches the top dead center is reduced. Therefore, the space (20b) for receiving the tip protruding from the holding bush (7) can be small, and the diameter of the swing compressor can be reduced accordingly.

At this time, the tapered portions (6w) and (6w) of the blade (6) are moved to a portion positioned at the position of the pivot axis (Q) when the piston (4) is located at the bottom dead center. In this case, the guide of the swinging motion of the blade (6) by the holding bush (7) is appropriate despite the provision of the tapered portions (6w) and (6w). Can be performed.

In the second embodiment, instead of the tapered portions (6h) and (6h) of the first embodiment, each of the direction of the pivot axis (Q) and the length of the blade (6) is orthogonal. The tapered portions (6w) and (6w) are provided on both sides in the direction of movement.
w) may be provided together.

[0043]

As described above, according to the first aspect of the present invention, the cylinder in which the suction port and the discharge port are opened in the cylinder chamber having a circular cross section and are opened in the circumferential direction is shifted from the cylinder chamber. A crank shaft having an eccentric shaft portion provided in the cylinder chamber and rotatably fitted around the eccentric shaft portion of the crank shaft, and the shaft being rotated by rotation of the crank shaft. A roller that revolves around the center, a piston having a rectangular cross-section blade integrally provided so as to protrude outward in the radial direction, and a suction port and a discharge port facing the cylinder chamber of the cylinder. And a retainer that is arranged at a position and holds the blade so as to swing about an axis parallel to the axis of the crankshaft and reciprocally move in the length direction of the blade. Since the tip of the blade is formed in a tapered shape in which the dimension in the direction of the pivot axis decreases toward the tip of the blade, the tip of the blade is moved from the bottom dead center to the top dead center by the piston. When the blade moves in the direction in which the blade advances to the holding body as it moves to the point, the wedge effect of the lubricating oil on the tapered portion can improve the oil film forming ability in the sliding portion thereof, and can improve the cylinder or holding capacity. It is possible to make it difficult for the blade tip to pry against the body,
The behavior of the piston can be stabilized. further,
Since the dimension of the piston end surface in the direction in which the blade extends can be shortened by the amount of the tapered portion, it is possible to easily obtain the accuracy of the piston in the axial direction. The gap can be reduced to increase compressor efficiency.

According to the second aspect of the present invention, the tapered portion of the blade is arranged at a position on the tip side from the blade portion positioned in the holding body when the piston is located at the bottom dead center. Leakage of the working fluid caused by the low-pressure chamber and the high-pressure chamber communicating with each other via the tapered portion can be avoided.

According to the third aspect of the present invention, in the swing compressor, the blade is provided such that the tip of the blade is positioned inside the holder when the piston is located at the bottom dead center. The tip of the blade is formed in a tapered shape in which the dimension in the direction of the pivot axis and in the direction perpendicular to each of the lengths of the blade decreases toward the tip of the blade. According to the present invention as well, the oil film forming ability can be improved, wrinkles caused by the edge of the blade tip can be made hard to occur, and the behavior of the piston can be stabilized. Furthermore, since the amount by which the tip of the blade penetrates the holding body when the piston reaches the top dead center can be reduced, the space for receiving the blade tip protruding from the holding body is reduced. The size of the swing compressor can be reduced, and the diameter of the swing compressor can be reduced accordingly.

According to the fourth aspect of the present invention, the tapered portion of the blade is disposed at a position on the tip side of the blade portion which is positioned at the pivot axis when the piston is located at the bottom dead center. With this configuration, it is possible to properly guide the swinging motion of the blade by the holding member, despite the provision of the tapered portion.

[Brief description of the drawings]

FIG. 1 is a perspective view schematically showing a piston of a swing compressor according to Embodiment 1 of the present invention.

FIG. 2 is a longitudinal sectional view showing the entire configuration of the swing compressor.

FIG. 3 is a sectional view taken along line III-III in FIG. 2;

FIG. 4 is a side view schematically showing the operation of a tapered portion of a blade.

FIG. 5 is a cross-sectional view showing a main part of a swing compressor according to Embodiment 2 of the present invention.

FIG. 6 is a view corresponding to FIG. 3 showing a main part of a conventional swing compressor.

FIG. 7 is a diagram corresponding to FIG. 1, schematically showing a main part of a conventional swing compressor.

[Explanation of symbols]

 (1) Cylinder (1a) Suction port (1b) Discharge port (2) Cylinder chamber (2a) Low pressure chamber (2b) High pressure chamber (3) Crankshaft (3a) Eccentric shaft (4) Piston (5) Roller (6) ) Blade (6h), (6w) Tapered part (7) Holding bush (holding body) (P) Axis (of crankshaft) (Q) Oscillating axis

Claims (4)

[Claims] 1. A cylinder (1) in which a suction port (1a) and a discharge port (1b) are opened in the cylinder chamber (2) having a circular cross section so as to be shifted in the circumferential direction, and penetrate the cylinder (1). A crankshaft (3) provided rotatably about an axis (P) in a deflected state and having an eccentric shaft (3a) in a cylinder chamber (2); and an eccentric shaft (3a) of the crankshaft (3). ), A blade (6) having a rectangular cross section is radially outwardly attached to a roller (5) rotatably fitted to the outer periphery of the roller (5) and revolving around the axis (P) by rotation of the crankshaft (3). And a piston (4) integrally provided so as to protrude toward the cylinder chamber (2) and a suction port (1a) and a discharge port (1b) facing the cylinder chamber (2) of the cylinder (1). And the blade (6) having an axis parallel to the axis (P) of the crankshaft (3). (Q) a holding body (7) for swinging around and reciprocally moving in the longitudinal direction of the blade (6), the blade (6) being revolved with the roller (5). ) And a low pressure chamber (2a) in a cylinder chamber (2) facing the suction port (1a).
The working fluid is sucked from the cylinder chamber (2), while the cylinder chamber (2) is partitioned by the blade (6) and faces the discharge port (1b).
In the swing compressor, the working fluid in the high-pressure chamber (2b) is discharged from the discharge port (1b), the tip of the blade (6) is dimensioned in the direction of the pivot axis (Q). Is formed in a tapered shape that becomes smaller toward the tip end side of the blade (6). 2. The swing compressor according to claim 1, wherein the piston is located at a bottom dead center.
A swing compressor characterized in that a portion from the blade (6) positioned inside to the tip side is formed in a tapered shape. 3. A cylinder (1) in which a suction port (1a) and a discharge port (1b) are opened in the cylinder chamber (2) having a circular cross section so as to be shifted in the circumferential direction, and penetrate the cylinder (1). A crankshaft (3) provided rotatably about an axis (P) in a deflected state and having an eccentric shaft (3a) in a cylinder chamber (2); and an eccentric shaft (3a) of the crankshaft (3). ), A blade (6) having a rectangular cross section is radially outwardly attached to a roller (5) rotatably fitted to the outer periphery of the roller (5) and revolving around the axis (P) by rotation of the crankshaft (3). And a piston (4) integrally provided so as to protrude toward the cylinder chamber (2) and a suction port (1a) and a discharge port (1b) facing the cylinder chamber (2) of the cylinder (1). And the blade (6) having an axis parallel to the axis (P) of the crankshaft (3). (Q) a holding body (7) for swinging around and reciprocally moving in the longitudinal direction of the blade (6), the blade (6) being revolved with the roller (5). ) And a low pressure chamber (2a) in a cylinder chamber (2) facing the suction port (1a).
The working fluid is sucked from the cylinder chamber (2), while the cylinder chamber (2) is partitioned by the blade (6) and faces the discharge port (1b).
In the swing compressor, the working fluid in the high-pressure chamber (2b) is discharged from the discharge port (1b). When the piston (4) is located at the bottom dead center, The tip of the blade (6) is provided so as to be positioned inside the holder (7), and the tip of the blade (6) is positioned in the direction of the pivot axis (Q) and the blade (6). A swing compressor characterized in that a dimension in a direction perpendicular to each of the length directions is formed in a tapered shape in which the dimension decreases toward a tip end side of the blade (6). 4. The swing compressor according to claim 3, wherein the piston (4) is located at the bottom dead center.
A swing compressor characterized in that a portion of the blade (6) positioned at the position of the swing axis (Q) in the inside is formed in a taper shape at a portion on the tip side.