JP2510079Y2 - Rolling piston type compressor - Google Patents

Description

[Detailed description of the device]

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling piston type compressor, and more particularly to improvement of measures for preventing fluid leakage around a roller.

[0002]

2. Description of the Related Art Generally, as one type of compressor provided in a refrigerator or the like, for example, a rolling piston type compressor as disclosed in Japanese Patent Laid-Open No. 63-167095 is known. This type of compressor is configured such that an electric motor and a compressor body connected to the electric motor via a crankshaft are housed in a casing. As shown in FIG. 4 , the compressor body is provided with a roller (b) as a rolling piston inside a cylinder (a), and a front head (on the upper and lower end faces of the cylinder (a)). c) and a rear head (d) are attached, and a compression chamber (not shown) is formed between the inner peripheral surface of the cylinder (a) and the outer peripheral surface of the roller (b). Also,
The crank shaft (e) extending from the electric motor is eccentric from the shaft center of the crank shaft (e), and the height dimension thereof is substantially the same as that of the roller (b) as shown by an imaginary line in FIG. The pin portion (f1) is integrally formed, and the pin portion (f
The roller (b) is eccentrically arranged with respect to the cylinder (a) by fitting 1) into the center of the roller (b). As a result, a part of the outer peripheral surface of the roller (b) contacts the inner peripheral surface of the cylinder (a). Further, the cylinder (a) is formed with a fluid suction path and a fluid discharge path, and a blade (g) is retractable into and from the compression chamber between the suction path and the discharge path. The compression chamber is divided into a high pressure chamber and a low pressure chamber by the tip end surface of the blade (g) being in contact with the outer peripheral surface of the roller (b).

When the compressor is driven, the rotation of the crankshaft (e) changes from the pin portion (f1) to the roller (b).
And the volume of the compression chamber is changed by the rotation of the roller (b) in the cylinder (a).
A fluid such as a refrigerant flows into the compression chamber, is compressed, and is then discharged from the discharge passage.

[0004]

In the operating state of the rolling piston compressor as described above, the outer peripheral surface of the pin portion (f1) of the crankshaft (e) is the inner peripheral surface of the roller (b). Since both (b) and (f1) slide on each other in a state where they are always in contact with the surface, mechanical loss due to this sliding is large, leading to a reduction in compressor efficiency. Therefore, there has been a demand for a structure that can reduce mechanical loss due to this sliding.

In view of this point, as shown by the solid line in FIG. 4, the height of the pin portion (f2) is reduced so that the pin portion (f2) is reduced.
It is conceivable to reduce the mechanical loss by reducing the sliding area between the outer peripheral surface of the roller (b) and the inner peripheral surface of the roller (b). It is difficult to rotate, and a new problem occurs such that the compressed fluid leaks in each part. That is, since the pin (f2) has a small height, the supporting area for supporting the roller (b) in a horizontal state becomes small, which causes the roller (b) to tilt during rotation . 4 , a gap between the upper end surface of the roller (b) and the front head (c) as indicated by the dimension (t1) in FIG.
A gap between the lower end surface of the roller (b) and the rear head (d) as shown by the dimension (t2), an outer peripheral surface of the roller (b) and an inner peripheral surface of the cylinder (a) as shown by the dimension (t3). A situation arises in which the gap between and becomes large and it becomes impossible to seal with oil. Therefore, there is a problem that the fluid leaks from the high pressure side to the low pressure side due to each of the gaps (t1), (t2), and (t3), the predetermined compression operation is not performed, and the compressor efficiency is significantly reduced. .

The present invention has been made in view of these points, and it is possible to reduce the sliding area between the pin portion (f2) and the roller (b) and to increase the clearance around the roller (b). It is an object of the present invention to obtain a configuration capable of satisfying the difficult requirements of prevention.

[0007]

In order to achieve the above-mentioned object, the present invention comprises a pin portion composed of a plurality of stages of thin-walled pins to reduce the sliding area between the pin portion and the roller. Positions near both end surfaces of the roller were determined by pins so that the roller did not tilt during rotation. Specifically, a casing (2) contains a drive means (3) and a compression means (4) linked to the drive means (3), and the compression means (4) is connected to a cylinder (5). An inner peripheral surface of the cylinder (5) and an outer periphery of the roller (6) are formed by accommodating a roller (6) therein and disposing head portions (7) and (8) on both end surfaces of the cylinder (5). It is formed by forming a compression chamber (9) with the surface. Also, by inserting an eccentric portion (12) formed in the roller (6) in a predetermined direction from the axis of the drive shaft (3b) of the drive means (3), the roller (6) is cylinder-loaded. The roller (6) is eccentrically arranged so that a part of the outer peripheral surface of the roller (6) is brought into contact with the inner peripheral surface of the cylinder (5). Then, a blade (11) which can be retracted into and out of the compression chamber (9) is disposed in the cylinder (5), and the tip end surface of the blade (11) contacts the outer peripheral surface of the roller (6). The compression chamber (9) is brought into contact with the low pressure chamber (9
It is divided into a) and a high pressure chamber (9b). Further, a fluid suction passage (5a) and a fluid discharge passage (5d) are connected to the compression chamber (9), and the roller (6) is moved within the cylinder (5) as the driving means (3) is driven. When rotating, the suction passage (5
It is premised on a rolling piston type compressor configured to suck a fluid from a) into the compression chamber (9) and compress the fluid. Then, the eccentric portion (12) is formed by a plurality of eccentric plates (12a), (12b) arranged at a predetermined interval in the extension direction of the drive shaft (3b), and each of the eccentric plates ( Drive shaft (3b) of 12a) and (12b)
Eccentric plates (12a), (12) located on both outer sides in the extension direction
b) One eccentric plate (12a) is positioned in the peripheral portion of one end surface of the roller (6), while the other eccentric plate (12b)
Is located around the other end surface of the roller (6) ,
High pressure chamber in a plurality of eccentric plates (12a), (12b)
When the inside of (9b) becomes high pressure, the high pressure chamber (9b)
Compare the thickness of the facing part to the thickness of other parts
The configuration is set large.

[0008]

With the above structure, in the present invention, the driving means (3)
The roller (6) of the compression means (4) rotates in the cylinder (5) as a result of the driving of the fluid, thereby causing the fluid to flow into the compression chamber (9) through the suction passage (5a) and compress the fluid. To do.
Then, the compressed fluid is discharged from the discharge passage (5d). In such an operating state, the eccentric plate (12
While the outer peripheral surfaces of a), (12b), ... And the inner peripheral surface of the roller (6) relatively slide, the eccentric plates (12a),
Rotational force is transmitted from the eccentric part (12) constituted by (12b), ... To the roller (6). Of the eccentric plates (12a), (12b), ..., the drive shaft (3
b) Eccentric plates (12a) located on both outer sides in the extension direction,
Since (12b) supports both end surfaces of the roller (6), the roller (6) is rotated without tilting, and the gap around the roller (6) becomes large so that fluid leaks. Disappears. Also, each eccentric plate (12a),
To sum the contact area between the outer peripheral surface and the inner peripheral surface of the roller (6) in (12b) is reduced, that has mechanical loss is reduced due to sliding between the two. Also, the high-pressure chamber (9
When the inside of b) becomes a high pressure state, the roller (6) is strongly pressed toward the eccentric part (12) by the fluid pressure in the high pressure chamber (9b). At this time, since the plate thickness dimension of each eccentric plate (12a), (12b) facing the high pressure chamber (9b) is set to be large, this pressure is applied by each eccentric plate (12a), (12b). It can be sufficiently accepted and a stable operating condition can be obtained.

[0009]

Embodiments of the present invention will now be described with reference to the drawings. As shown in FIG. 1, a rolling piston compressor (1) according to the present invention is constructed by housing a drive means (3) and a compressor body (4) as a compression means in a casing (2). ing.

The drive means (3) comprises an electric motor (3a) and a crankshaft (3b) as a drive shaft.
The electric motor (3a) is disposed above the internal space (2a) of the casing (2), and the stator (3c) fixed to the inner peripheral surface of the casing (2) and the stator (3).
c) and a rotor (3d) arranged in the central portion. The crankshaft (3b) has its upper end connected to the center of the rotor (3d), and has its lower end extended downward and linked to the compressor body (4). Lubricating oil (O) is stored in the bottom of the casing (2), and the lower end of the crankshaft (3b) is immersed in the lubricating oil (O). A centrifugal pump (3e) is arranged at the lower end of the crankshaft (3b), and an oil supply passage (not shown) extending in the vertical direction is formed through the crankshaft (3b).
When the compressor (1) is driven, the lubricating oil (O) is pumped to the oil supply passage by the centrifugal pump (3e) and then supplied to each sliding portion of the compressor (1). .

On the other hand, the compressor body (4) has a fixed blade shape and is arranged below the electric motor (3a). As shown in FIGS. 1 and 2, the compressor body (4) has rollers (6) housed in a cylindrical cylinder (5) fixed to the inner wall of the casing (2). A front head (7) as a head portion is mounted on the upper end surface of the cylinder (5), and a rear head (8) as a head portion is also mounted on the lower end surface thereof. The front head (7) and the rear head (8) ), A compression chamber (9) is formed between the inner peripheral surface of the cylinder (5) and the outer peripheral surface of the roller (6). The front and rear heads (7), (8) have the crankshaft (3
b) through holes (7a), (8a) which are formed to have a diameter substantially the same as the diameter of b) and extend in the vertical direction.
A crank shaft (3b) is rotatably supported by (8a) via a metal seal or the like. In addition, the cylinder (5) has a refrigerant suction passage (5) which opens to the compression chamber (9).
a) is formed, and a suction pipe (10) extending from an accumulator (not shown) is connected to the suction passage (5a). On the other hand, at the center of the roller (6), the crankshaft (3b) is formed integrally with the crankshaft (3b).
A pin portion (12) as an eccentric portion, which is a characteristic member of the present invention and is eccentric in a predetermined direction with respect to the axial center of (4), is inserted (details will be described later). Thereby, the roller (6) is provided eccentrically with respect to the cylinder (5),
A part of the outer peripheral surface of the roller (6) is always in contact with the inner peripheral surface of the cylinder (5).

A blade groove (5) is provided in the vicinity of the position of the suction passage (5a) in the cylinder (5).
b) is formed. The blade groove (5b) extends in the radial direction of the cylinder (5), penetrates the upper and lower end surfaces of the cylinder (5), and the outer peripheral side thereof is the internal space (2a) of the casing (2). ) Is in communication with. The blade (11) is inserted into and retracted from the cylinder (5) in the blade groove (5b). In the blade (11), the urging force of the spring (13) arranged between the back surface (11a) and the blade groove (5b) and the fluid pressure in the internal space (2a) of the casing (2) are reduced. By acting on the back surface (11a), the tip surface of the roller (6) is
The compression chamber (9) is pressed against the outer peripheral surface of the low pressure chamber (9
It is divided into a) and a high pressure chamber (9b).

A discharge passage (5d) is provided on the high pressure chamber (9b) side of the position where the blade (11) is arranged. One end of the discharge passage (5d) is opened to the inner peripheral surface of the cylinder (5), and the high pressure chamber (9
A reed valve (not shown) that can be opened when the pressure in b) increases is provided. On the other hand, the other end of the discharge passage (5d) is opened to the internal space (2a) of the casing (2). A discharge pipe (14) connected to a condenser (not shown) is connected to the upper surface of the casing (2), and the high temperature and high pressure refrigerant discharged from the compressor body (4) is discharged from the discharge pipe (14). Is led to the condenser side. With this configuration, when the compressor is driven, the crank shaft (3) driven by the electric motor (3a) is driven.
With the rotation of b), the roller (6) moves to the cylinder (5).
The compression chambers (9a), (9b) are contracted by rotating inside.

Next, the characteristic configuration of this example will be described. As described above, the characteristic feature of the present example is that the pin portion (12) integrally formed with the crankshaft (3b).
In the configuration. As shown in FIGS. 1 and 3, the pin portion (12) is referred to in the present invention, which is installed side by side with a predetermined interval in the extension direction of the crankshaft (3b), that is, the vertical direction in FIGS. 1 and 3. It is composed of a first pin (12a) and a second pin (12b) as an eccentric plate. 1st pin (12
a) is arranged inside the roller (6) at a position near the upper end surface of the roller (6), and its outer peripheral surface is arranged so as to contact the inner peripheral surface of the roller (6). . On the other hand, the second pin (12b) is arranged inside the roller (6) at a position near the lower end surface of the roller (6) and is eccentric in the same direction as the first pin (12a), The outer peripheral surface is arranged so as to contact the inner peripheral surface of the roller (6). With such a configuration, the roller (6) is supported by the first pin (12a) and the second pin (12b) at positions near both upper and lower end surfaces thereof, and the horizontal state can be maintained. There is. In other words, such a structure of the pin portion (12) exerts the same supporting function as that of the conventional pin portion having a height dimension ranging from the position near the upper end face to the position near the lower end face of the roller (6) as in the prior art. Not only is it made of rollers (6)
The total area of contact with the inner peripheral surface of is small.

Regarding the shape of the pin portion (12)
More specifically, as shown in FIG. 3, the pin portion (1
In 2), a part of the first pin (12a) and the second pin (12b) is formed to have a large height. That is, in the first pin (12a), the lower surface of only the portion facing the high pressure chamber (9b) when the inside of the high pressure chamber (9b) is in the high pressure state in the operating state of the compressor (1). (12d)
Is moved slightly downward through the inclined portion (12e), and the height dimension of this portion is set to be slightly larger (dimension T in FIG. 3 ) .
1) Has been done. On the other hand, in the second pin (12b), the high pressure chamber (9
When the inside of b) becomes a high pressure state, the upper surface (12f) of only the portion facing the high pressure chamber (9b) is slightly moved upward through the inclined portion (12g), and the height dimension of this portion is changed. It is set to be slightly larger (dimension T2 in FIG. 3 ).

Next, the operation of the rolling piston compressor (1) will be described. First, when the electric motor (3a) is driven, this driving force is applied to the crankshaft (3
It is transmitted to the roller (6) of the compressor body (4) through the pin portion (12) of b), and the roller (6) rotates in the cylinder (5) so as to contract the compression chamber (9). . As a result, the refrigerant gas flows from the suction pipe (10) into the low pressure chamber (9a) of the compressor body (4) through the suction passage (5a). Then, as the roller (6) rotates, the refrigerant gas is compressed as the low-pressure chamber (9a) becomes the high-pressure chamber (9b), and when the pressure of the refrigerant gas reaches a predetermined value, the pressure causes the lead to flow. The valve is opened, and the high-pressure refrigerant gas is discharged from the discharge passage (5d) to the internal space (2a) of the casing (2), and then discharged to the condenser side by the discharge pipe (14). In such an operating state, the internal space (2a) of the casing (2) is in a high pressure atmosphere.
In addition, the lubricating oil (O) pumped to the oil supply passage by the centrifugal pump (3e) as the crankshaft (3b) rotates.
Is supplied to each sliding part in the compressor (1) to lubricate each part.

In such an operating state, the outer peripheral surfaces of the first and second pins (12a) and (12b) and the roller (6).
The rotational force is transmitted while sliding relative to the inner peripheral surface of the. At this time, the first and second pins (12a),
Since (12b) supports the positions near the upper and lower end surfaces of the roller (6) and allows the roller (6) to rotate while maintaining the horizontal state, the roller (6) is tilted ( Fig.
4 ), gaps between the upper and lower end surfaces of the roller (6) and the front and rear heads (7) and (8), and between the outer peripheral surface of the roller (6) and the inner peripheral surface of the cylinder (5). It is possible to prevent the gaps from becoming large, and these gaps can be reliably sealed by the lubricating oil (O) to perform a predetermined compression operation. In addition, each pin (12a), (1
Since the height dimension of 2b) is small, the total contact area between the outer peripheral surface of each pin (12a), (12b) and the inner peripheral surface of the roller (6) is small. The mechanical loss due to the sliding between the two is small.

Therefore, it is possible to obtain both the suppression of the refrigerant leakage from the high pressure side to the low pressure side around the roller (6) and the suppression of the mechanical loss due to the sliding, which are not compatible with the conventional structure, with a simple structure. Both of them can significantly improve the efficiency of the compressor.

Further , as described above, the first pin (12
a) and the high pressure chamber (9b) at the second pin (12b)
Make sure that the height of only the facing parts is large.
Thus, during operation of the compressor (1), the high pressure chamber (9
When the inside of b) becomes a high pressure state, the roller (6) is strongly pressed toward the pin portion (12) by the fluid pressure in the high pressure chamber (9b). 1
Since the height dimensions of 2a) and (12b) are large, this pressure can be sufficiently received and a stable operating state can be obtained. Moreover, not only that, but since the inclined portions (12e) and (12g) are formed on the respective pins (12a) and (12b),
The space (S) formed between the first pin (12a) and the second pin (12b) acts as a fluid nozzle, and the oil pressure of the lubricating oil existing in this space (S) is increased, Due to this pressure, the high pressure chamber (9
It is also possible to obtain a supporting force that opposes the refrigerant pressure in b). For this reason, mechanical loss due to sliding between the inner peripheral surface of the roller (6) and the pin portion (12) is reduced, and the compressor efficiency can be further improved.

Although the above-mentioned embodiments have been described with respect to the compressor provided in the air conditioner, the present invention is not limited to this.
It is applicable to various fluid compressors.

Further , the first pin (12a) and the second pin (1
One or a plurality of individual intermediate pins at the intermediate position with 2b)
More reliable maintenance of the horizontal state of the roller (6) by providing one
You may be able to perform.

[0022]

As described above, according to the present invention, the eccentric part (12) for transmitting the rotational force of the drive shaft (3b) to the roller (6) is provided in the extending direction of the drive shaft (3b). A plurality of eccentric plates (12a), (12) arranged at intervals.
b), each of the eccentric plates (12a), (12)
One of the eccentric plates (12a), (12b) located on both outer sides in the extension direction of the drive shaft (3b) in b).
a) is positioned near the one end surface of the roller (6), while the other eccentric plate (12b) is positioned near the other end surface of the roller (6).
2) The total sliding area between the roller (6) and the roller (6) is reduced to reduce mechanical loss due to sliding between the eccentric part (12) and the roller (6), and at the same time, the eccentric plates (12a), (12b), By supporting the peripheral portions of both end surfaces of the roller (6) by ..., the inclination of the roller (6) is prevented and the leakage of fluid around the roller (6) is suppressed. It is possible to obtain both the suppression of mechanical loss due to sliding which is not obtained and the suppression of fluid leakage around the roller (6) with a simple structure. Together, these both aim to greatly improve the efficiency of the compressor. be able to.

Further, eccentric plate (12a), a (12b),
When the high pressure chamber (9b) is in a high pressure state, the high pressure chamber (9b)
The eccentricity is set when the inside of the high pressure chamber (9b) is in a high pressure state during compressor operation by setting the thickness of the portion facing b) larger than the thickness of the other portion. Since the plates (12a) and (12b) can sufficiently receive this pressure, a more stable operating state can be obtained.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a rolling piston compressor according to an embodiment.

FIG. 2 is a cross-sectional view at a position corresponding to line II-II in FIG.

FIG. 3 is a vertical cross-sectional view around the compressor body.

FIG. 4 is a view corresponding to FIG. 3 in a conventional example.

[Explanation of symbols]

 (1) Rolling piston type compressor (2) Casing (3) Drive means (3b) Crankshaft (drive shaft) (4) Compressor body (compression means) (5) Cylinder (5a) Suction path (5d) Discharge path (6) Roller (7) Front head (head portion) (8) Rear head (head portion) (9) Compression chamber (9a) Low pressure chamber (9b) High pressure chamber (11) Blade (12) Pin portion (eccentric portion) ( 12a) 1st pin (eccentric plate) (12b) 2nd pin (eccentric plate)

Claims (1)

(57) [Scope of utility model registration request] 1. A drive means (3) in the casing (2).
And a compression means (4) connected to the driving means (3) are housed, and the compression means (4) contains a roller (6) in a cylinder (5) and the cylinder (5).
Head portions (7) and (8) are disposed on both end surfaces of the cylinder, and a compression chamber (9) is formed between the inner peripheral surface of the cylinder (5) and the outer peripheral surface of the roller (6). The roller (6) has an eccentric portion (12) formed eccentrically in a predetermined direction from the axis of the drive shaft (3b) of the drive means (3), so that the roller (6) is inserted.
Is eccentric with respect to the cylinder (5), and a part of the outer peripheral surface of the roller (6) abuts on the inner peripheral surface of the cylinder (5). 9) is provided with a blade (11) which can be freely retracted and retracted, and the tip end surface of the blade (11) is brought into contact with the outer peripheral surface of the roller (6), so that the compression chamber (9) has a low pressure. Chamber (9a) and high pressure chamber (9
b), a fluid suction passage (5a) and a fluid discharge passage (5d) are connected to the compression chamber (9), and a roller (3) is driven by the driving means (3). 6) A rolling piston compressor in which 6) is configured to rotate in the cylinder (5) to suck the fluid from the suction passage (5a) into the compression chamber (9) and compress the fluid. The eccentric part (12) includes a plurality of eccentric plates (12) arranged at predetermined intervals in the extension direction of the drive shaft (3b).
a) and (12b), and among the eccentric plates (12a) and (12b), the eccentric plates (12a) and (12b) located on both outer sides in the extending direction of the drive shaft (3b) are
While one of the eccentric plate (12a) is positioned on one end face periphery of the roller (6), the other eccentric plate (12b) are located at the other end face periphery of the roller (6), this
The plurality of eccentric plates (12a) and (12b) are high pressure chambers.
When the inside of (9b) becomes high pressure, the high pressure chamber (9b)
The thickness of the facing part is larger than the thickness of other parts
A rolling piston compressor characterized by being set large .