JPH05157073A - Rolling piston type compressor - Google Patents

Abstract

PURPOSE:To reduce mechanical loss due to interlocking between a blade and a roller by providing a fluid switching means for switching fluid pressure working on the back of the blade according to the rotational position of the roller, and by having low pressure worked on the back at a bottom dead center of the roller. CONSTITUTION:When a roller 6 is rotated eccentrically in a cylinder 5 by the driving of an electric motor 3, a referigerant gas attracted by an inlet tube 10 is compressed, and is discharged out of a discharge route 5d with a lead valve pushed open. At this time, when the roller 6 is at a bottom dead center, a blade 11 is put in a blade groove 5b, and the opening part of a low pressure guiding route 19 is closed by the blade 11, while the opening part of a high pressure guiding route 18 is opened into a high pressure guiding space 15 and high pressure is guided to a back pressure space 12, and the blade 11 is pressed to the peripheral surface of the roller 6. At the bottom dead center, the high pressure guiding route 18 is closed, and the low pressure guiding route 19 is opened, and low pressure is guided to the back pressure space 12, and interlocking resistance between the blade 11 and the roller 6 is thus reduced.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling piston type compressor, and more particularly to measures for reducing mechanical loss due to sliding between a roller outer peripheral surface and a blade tip surface.

[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. 8, the compressor body has rollers (b) as rolling pistons arranged in a cylinder (a), and a front (not shown) on each of the upper and lower end surfaces of the cylinder (a). A head and a rear head are attached, and a compression chamber (c) is formed between the inner peripheral surface of the cylinder (a) and the outer peripheral surface of the roller (b). The roller (b) is eccentrically arranged with respect to the cylinder (a) because a cam portion of a crank shaft extending from the electric motor is fitted therein. 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 provided with a fluid suction passage (d) and a fluid discharge passage (e), and a blade () is provided between the suction passage (d) and the discharge passage (e). f) is the compression chamber (c)
The blade (f) is provided so as to be able to project and retract inside, and the tip end surface of the blade (f) is brought into contact with the outer peripheral surface of the roller (b) so that the compression chamber (c) becomes the high pressure chamber (c1). It is partitioned into a low pressure chamber (c2).

When the compressor is driven, the roller (b) rotates with the rotation of the crankshaft (arrow A in FIG. 8).
By changing the volumes of the compression chambers (c1) and (c2) by means of the above, a fluid such as a refrigerant flows from the suction passage (d) into the compression chamber (c), and after compressing the fluid, the discharge passage ( The discharge is performed from e).

Further, in order to divide the high pressure chamber (c1) and the low pressure chamber (c2) by the blade (f), the back side of the blade (f) is given a biasing force toward the roller (b). Not only is the spring (g) provided, but a portion of the compressed and high-pressure fluid is guided to the back side of the blade (f) (arrow B in FIG. 8), and this blade back side A high pressure is applied to the blade (f) to press the tip surface of the blade (f) against the outer peripheral surface of the roller (b).

[0005]

As described above, in the rolling piston compressor, the tip end surface of the blade (f) and the outer peripheral surface of the roller (b) are always in contact with each other, and the blade ( In f), since a large urging force toward the roller (b) side is constantly given by the spring (g) and the fluid pressure (B), mechanical loss due to sliding between these two (b) and (f) Was large, leading to a reduction in compressor efficiency.

In view of this point, it is conceivable to set the urging force applied to the blade (f) to a low value. However, in this case, the high pressure chamber (c1) and the low pressure chamber (c2) are sufficiently divided. Sometimes there is not. That is, the pressure in the high pressure chamber (c1) is considerably high in the rotating state of the roller (b) as indicated by the phantom line in FIG. 8, and at this time, as described above, the biasing force is set to be low. , The pressure in the high pressure chamber (c1) overcomes the urging force of the spring (g) and the fluid pressure (B), and the tip surface of the blade (f) is separated from the outer peripheral surface of the roller (b). ) And the low-pressure chamber (c2) communicate with each other, and a predetermined compression operation may not be performed.

Therefore, the inventors of the present invention have found that when the roller (b) is rotated from the top dead center to the bottom dead center (the state shown by the solid line in FIG. 8), the roller (b) moves to the blade (f).
Therefore, the blade (f) follows the rotational movement of the roller (b) by securing a large biasing force by the spring (g) and the fluid pressure (B). It is necessary to keep it, but in the rotating state from the bottom dead center to the top dead center, the roller (b) is in the state of moving toward the blade (f). Therefore, in this state, inside the high pressure chamber (c1) When the pressure is not yet high, even if the biasing force of the spring (g) and the fluid pressure (B) is relatively small, each chamber (c) of the blade (f) is
We paid attention to the fact that the divisions of 1) and (c2) can be reliably performed.

The present invention has been made in view of this point, and in a state where the roller rotates from the bottom dead center to the top dead center, sliding between the blade tip surface and the roller outer peripheral surface is performed. The purpose is to reduce the mechanical loss due to.

[0009]

In order to achieve the above-mentioned object, the present invention makes variable the fluid pressure acting on the back side of the blade depending on the retracted and moved position of the blade according to the rotation of the roller. did. Specifically, the invention according to claim 1 accommodates a drive means (3) and a compression means (4) connected to the drive means (3) in a casing (2),
The cylinder (5) is formed by accommodating the roller (6) in the cylinder (5) and disposing the head portions (7) and (8) on both end surfaces of the cylinder (5). 2) and the outer peripheral surface of the roller (6), a compression chamber (9) is formed. Also, by inserting an eccentric part (3f) 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 moved to the cylinder. 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). Furthermore, the cylinder (5)
In addition, the blade (1
1) is provided, and by applying fluid pressure to the back surface (11a) of the blade (11), the tip end surface of the blade (11) is pressed against the outer peripheral surface of the rotor (6), and the compression chamber (9) is removed. It is divided into a low pressure chamber (9a) and a high pressure chamber (9b). And
A fluid suction passage (5a) and a fluid discharge passage (5d) are connected to the compression chamber (9), and the roller (6) is rotated in the cylinder (5) as the driving means (3) is driven. Then, it is premised on the rolling piston type compressor configured to suck the fluid from the suction passage (5a) into the compression chamber (9) and compress the fluid. And the roller (6)
Of the blade (11) according to the rotational position of the blade (11).
The fluid pressure acting on a) is switched between high pressure and low pressure, and at least at the top dead center of the roller (6), the rear surface (11a)
A fluid pressure switching means (20) that applies a high pressure to the rear surface (11a) of the roller (6) at least at the bottom dead center is provided.

According to a second aspect of the present invention, in the rolling piston compressor according to the first aspect, the blade (1
1) Blade groove (5b) formed in cylinder (5)
The blade groove (5b) and the blade (1
A back pressure space (12) is formed between the back surface (11a) of 1). Then, the fluid pressure switching means (20) is used to introduce the fluid pressure in the casing internal space (2a) into the back pressure space (12) and the fluid pressure in the suction passage (5a) to the back pressure space. Low-pressure introduction passage (19) introduced into (12)
I was prepared to do so.

According to a third aspect of the present invention, in the rolling piston compressor according to the first aspect, the blade (1
1) Blade groove (5b) formed in cylinder (5)
The blade groove (5b) and the blade (1
A back pressure space (12) is formed between the back surface (11a) of 1). Then, the fluid pressure switching means (20) is used to introduce the fluid pressure in the casing internal space (2a) into the back pressure space (12) and the fluid pressure in the low pressure chamber (9a) into the back pressure space. The low-pressure introduction path (21) introduced into (12) is provided.

[0012]

With the above construction, the present invention has the following effects. In the invention according to claim 1, the roller (6) of the compression means (4) rotates in the cylinder (5) as the drive means (3) is driven, whereby the compression chamber passes through the suction passage (5a). (9) A fluid is flown into and compressed. Thereafter, the compressed fluid is discharged through the discharge passage (5
It is discharged from d) into the internal space (2a) of the casing (2). With this operation, at least in the top dead center state of the roller (6), a high pressure is applied to the back surface (11a) of the blade (11) by the fluid pressure switching means (20). As a result, the tip end surface of the blade (11) is pressed against the outer peripheral surface of the roller (6) with a high pressure, so that the low pressure chamber (9a) and the high pressure chamber (9b) can be reliably partitioned. Then, the action of the compressed fluid acting from the high pressure chamber (9b) does not cause the blade (11) to separate from the outer peripheral surface of the roller (6). On the other hand, at least in the state of the bottom dead center of the roller (6), a low pressure is applied to the back surface (11a) of the blade (11) by the fluid pressure switching means (20). As a result, the pressing force of the blade (11) at the bottom dead center of the roller (6) is set to be low, and the mechanical force caused by sliding between the tip surface of the blade (11) and the outer peripheral surface of the roller (6). Losses are reduced. When the roller (6) rotates from the bottom dead center state to the top dead center state,
Since the roller (6) is to move in the direction close to the blade (11), the blade (1
Even if the pressing force of 1) is slight, the blade (11) is not separated from the roller (6). Further, at this time, since the pressing force of the blade (11) acting in the direction of inhibiting the rotation of the roller (6) is low, the rotation of the roller (6) is smoothly performed.

According to the second aspect of the invention, the back pressure space (1
When introducing high pressure into 2), the fluid pressure in the casing internal space (2a) is introduced through the high pressure introducing passage (18). On the other hand, when introducing low pressure into the back pressure space (12),
The fluid pressure in the suction passage (5a) is introduced by the low pressure introduction passage (19). Therefore, the difference between the high pressure and the low pressure introduced into the back pressure space (12) can be made large, and the mechanical loss at the time of introducing the low pressure is significantly reduced.

According to the third aspect of the invention, the back pressure space (1
When introducing high pressure into 2), the fluid pressure in the casing internal space (2a) is introduced through the high pressure introducing passage (18). On the other hand, when introducing low pressure into the back pressure space (12),
The fluid pressure in the low pressure chamber (9a) is introduced by the low pressure introduction passage (21). Therefore, it is not necessary to form a passage for introducing low pressure in the cylinder (5), and a means for introducing low pressure can be obtained with a simple structure.

[0015]

【Example】

(First Embodiment) Next, a first embodiment according to the present invention will be described with reference to the drawings. As shown in FIG. 1, a rolling piston compressor (1) according to the present invention
Is constituted by housing a drive means (3) and a compressor body (4) as a compression means in a casing (2).

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 attached to the upper end surface of the cylinder (5), and a rear head (8) as a head portion is attached to the lower end surface thereof, respectively. 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) having a diameter substantially the same as the diameter of b) and extending in the vertical direction are formed.
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 crank shaft (3b) is formed integrally with the crank shaft (3b).
A cam portion (3f) as an eccentric portion, which is eccentric in a predetermined direction with respect to the axial center of, is fitted. Thereby, the roller (6) is eccentrically provided with respect to the cylinder (5), and 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 both upper and lower end surfaces of the cylinder (5), and its outer peripheral side is closed by an outer peripheral wall (5c). .. Then, a blade (11), which is one of the characteristic members of this example, is inserted into and retracted from the inside of the cylinder (5) in the blade groove (5b). The blade (11) has its rear surface (1
1a) and the blade groove (5b) between the back pressure space (1
2) to form the back pressure space (12).
The tip end surface of the compression chamber (9) is pressed against the outer peripheral surface of the roller (6) by the urging force of the spring (13) disposed inside the compression chamber (9) and the high pressure chamber (9a) and the high pressure chamber (9b). It is divided into

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) rises 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) and (9b) are contracted by rotating inside.

Next, the characteristic part of this example will be described. The characteristic configuration of this example is the configuration around the blade (11) and the position where the blade (11) is disposed. First, the configuration of the blade (11) will be described. 3 showing this blade (11), FIG. 3 (a) is a sectional view taken along line III-III in FIG. 3 (c), and FIG.
3B is a rear view of the blade 11, and FIG. 3C is a side view of the blade 11. As shown in the figure, the blade (11) is provided on both left and right side surfaces (11b),
First and second recesses (11d) symmetrical to (11c),
(11e) is formed. The first recess (11d) is formed on the left side surface (11b) of the blade (11),
The upper surface (11) of the blade (11) is approximately at the central portion in the blade longitudinal direction (the left-right direction in FIG. 3A).
From the f) to the lower surface (11g), the left side surface (11
Part of b) is formed by cutting out. On the other hand, the second recess (11e) is formed on the right side surface (11c) of the blade (11), and like the first recess (11d), the blade (1) is formed at a substantially central portion in the blade longitudinal direction.
A part of the right side surface (11c) is cut out from the upper surface (11f) to the lower surface (11g) of 1). As a result, when the blade (11) is inserted into the blade groove (5b) as shown in FIG.
A high pressure introducing space (15) is formed between the recess (11d) and the blade groove (5b), and a low pressure introducing space (16) is formed between the second recess (11e) and the blade groove (5b). Are formed.

Further, inside the blade (11), pressure introducing passages (17) are formed at three positions spaced by a predetermined distance in the height direction of the blade (11). The pressure introducing passage (17) is provided with a first passage (17a) and a second passage (17).
It consists of b). The first passage (17a) is the first
And the second recesses (11d) and (11e) in the vicinity of the front ends thereof are formed so as to extend in the width direction of the blade (11) (vertical direction in FIG. 3A), and one end thereof is formed into the high pressure introducing space ( 15), and the other end opens into the low pressure introduction space (16). That is, the high pressure introduction space (15) and the low pressure introduction space (1
6) is communicated with the first passage (17a). On the other hand, the second passage (17b) is formed to extend in the longitudinal direction of the blade (11),
One end is open to the first passage (17a),
The other end is open to the back surface (11a) of the blade (11). Since the first passage (17a) and the second passage (17b) are formed in this manner, the high pressure introduction space (15) and the low pressure introduction space (16) pass through the pressure introduction passage (17). It is adapted to communicate with the back pressure space (12).

Next, the characteristic structure of this example in the peripheral structure of the arrangement position of the blade (11) will be described. As shown in FIG. 2, a high pressure introduction passage (18) and a low pressure introduction passage (19) are provided around the position where the blade (11) is arranged.

The high pressure introducing passage (18) has one end passing through the outer peripheral portion of the cylinder (5) and passing through the inner space (2) of the casing (2).
The blade groove (5b) is opened at a predetermined position on one side surface of the blade groove (5b).
The opening position at the other end is the high pressure introduction state in a state where the roller (6) at which the amount of protrusion of the blade (11) into the compression chamber (9) is at the top dead center (the state shown in FIG. 4). While the roller (6) is opened to the space (15) and the projection amount of the blade (11) into the compression chamber (9) is maximum, the roller (6) is at the bottom dead center (state shown in FIG. 5).
The position is set such that it is closed by the left side surface (11b) of 1).

The low-pressure introducing passageway (19) has one end opening to the suction passageway (5a) and the other end opening to a predetermined position on one side surface of the blade groove (5b). Then, the opening position at the other end of the blade (11) is in the state where the roller (6) at which the amount of protrusion of the blade (11) into the compression chamber (9) is at the top dead center (state shown in FIG. 4). )
In the state where the roller (6) that is closed by the right side surface (11c) of the blade (11c) and has the maximum amount of protrusion of the blade (11) into the compression chamber (9) is at the bottom dead center (the state shown in FIG. 5), It is set at a position such that it opens into the low pressure introduction space (16).

By thus providing the high pressure introduction passage (18) and the low pressure introduction passage (19), the casing (in the state shown in FIG. 4) of the roller (6) at the top dead center (the state shown in FIG. 4) is While the high pressure in the internal space (2a) of 2) is introduced into the back pressure space (12) through the high pressure introduction passage (18), the high pressure introduction space (15) and the pressure introduction passage (17). In the state where the roller (6) is at the bottom dead center (the state shown in FIG. 5), the low pressure in the suction passage (5a) causes the low pressure introduction passage (19), the low pressure introduction space (16) and the pressure introduction passage (17). And is introduced into the back pressure space (12). That is, at the roller top dead center, a large biasing force of the blade (11) to the roller (6) is secured, while at the roller bottom dead center, the blade (11) is pressed to the roller (6). It is configured to reduce the power. The fluid pressure switching means (20) according to the present invention is constituted by such a constitution.

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 (3a).
It is transmitted to the roller (6) of the compressor body (4) via the cam portion (3f) 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.

Next, the characteristic operation of this example will be described.
In the compressor (1) in the operating state as described above, when the roller (6) is at the top dead center as shown in FIG. 4, the blade (11) is immersed in the blade groove (5b). ing. In this state, the opening portion at one end of the low pressure introduction passage (19) is closed by the right side surface (11c) of the blade (11), while the opening portion at one end of the high pressure introduction passage (18) is the high pressure introduction passage. Space (1
5) is opened. Thereby, the high pressure in the internal space (2a) of the casing (2) is introduced into the back pressure space (12) through the high pressure introduction passage (18), the high pressure introduction space (15) and the pressure introduction passage (17). The back pressure space (12) becomes a high pressure atmosphere, and the introduced high pressure acts on the back surface (11a) of the blade (11) in addition to the urging force of the spring (13). Therefore, the tip end surface of the blade (11) is pressed against the outer peripheral surface of the roller (6) with a high pressure, so that the low pressure chamber (9a) and the high pressure chamber (9b) can be reliably partitioned. Therefore, the action of the compressed refrigerant acting from the high pressure chamber (9b) does not cause the blade (11) to separate from the outer peripheral surface of the roller (6). From this state, the roller (6) rotates (arrow C in FIG. 2), and the blade (11) projects and moves along the blade groove (5 b) with this rotation,
As shown in FIG. 5, when the roller (6) reaches the bottom dead center, the protrusion amount of the blade (11) becomes maximum. Then, in this state, the opening portion at one end of the high pressure introduction passage (18) is closed by the left side surface (11b) of the blade (11), while the opening portion at one end of the low pressure introduction passage (19) is the low pressure introduction passage. The space (16) is opened. As a result, the low pressure in the suction passage (5a) is introduced into the back pressure space (12) via the low pressure introduction passageway (19), the low pressure introduction space (16) and the pressure introduction passageway (17). Pressure space (1
2) becomes a low pressure atmosphere and the back surface (1) of the blade (11)
The urging force of the spring (13) and a slight fluid pressure (approximately atmospheric pressure) act on 1a). Therefore, the pressing force of the blade (11) on the roller (6) is set low. In this way, the difference between the high pressure (the discharge pressure in the casing) and the low pressure (suction pressure) introduced into the back pressure space (12) is made large, and the blade (11) is pushed at the bottom dead center of the roller (6). By setting the pressure to be low, mechanical loss due to sliding between the tip surface of the blade (11) and the outer peripheral surface of the roller (6) is reduced.
When the roller (6) further rotates from this state, the roller (6) moves in a direction closer to the blade (11), and thus the pressing force of the blade (11) is small. However, the blade (11) is not separated from the roller (6). Also, at this time,
The blade (1 that acts in the direction that impedes the rotation of the roller (6)
Since the pressing force of 1) is low, the roller (6) rotates smoothly, and the outer peripheral surface of the cam portion (3f) of the crankshaft (3b) and the inner peripheral surface of the roller (6) slide. Mechanical loss due to is also reduced.

As described above, according to the configuration of the present embodiment, by switching the fluid pressure acting on the back surface (11a) of the blade (11), the blade (11) can be operated without disturbing the operating state of the compressor. By reducing the average value of the pressing force of (1) on the roller (6), the mechanical loss due to sliding can be significantly reduced, and the compressor efficiency can be improved.

(Modification) Next, a modification of the above-described first embodiment will be described. This example is a modification of the blade (11) and the peripheral structure of the blade (11), and since the other configurations are similar to those of the above-described first example, the description thereof is omitted, and the features of this example Only the configuration to be described will be described here.

As shown in FIG. 6, the blade (1
1) and its surrounding structure, the high pressure introduction passage (1
8) and the high-pressure introducing space (15) are configured in the same manner as in the first embodiment described above, and the slit (5e) is formed at a predetermined position of the blade groove (5b). The position of forming the slit (5e) will be described with reference to FIG.
In the state where the roller (6) is at the top dead center as shown in (a), the front end portion (lower end portion in FIG. 6) of this slit (5e) faces the high pressure introducing space (15) and then The end portion (upper end portion in FIG. 6) is set to face the back pressure space (12). Further, in the state where the roller (6) is at the bottom dead center as shown in FIG. 6 (b), the front end of the slit (5e) does not face the high pressure introducing space (15) and the blade (11 ) Is set so as to face the left side surface (11b) or face the back pressure space (12).

On the other hand, the low pressure introduction passage (19) of this embodiment is located on the outer peripheral side of the cylinder (5) as compared with the first embodiment described above. Then, this low pressure introduction passage (1
The opening position of 9) on the blade groove (5b) side is shown in FIG.
When the roller (6) as shown in (a) is at the top dead center, the roller (6) as shown in FIG. 6 (b) is blocked by the right side surface (11c) of the blade (11). At the bottom dead center, the back pressure space (12) is set to face.

When the compressor of this example is driven,
As shown in FIG. 6A, when the roller (6) is at the top dead center, one end of the low pressure introduction passage (19) is blocked by the right side surface (11c) of the blade (11) while the high pressure introduction passage ( 18) communicates with the high pressure introduction space (15), the front end of the slit (5e) communicates with the high pressure introduction passage (15), and the rear end of the slit (5e) communicates with the back pressure space (12). is doing. As a result, the high pressure in the internal space (2a) of the casing (2) passes through the high pressure introducing passage (18), the high pressure introducing space (15) and the slit (5e), and the back pressure space (1).
Introduced into 2), a high pressure is applied to the back surface (11a) of the blade (11). On the other hand, as shown in FIG. 6B, when the roller (6) is at the bottom dead center, the high pressure introduction passage (18)
The opening at one end of the blade is closed by the left side surface (11b) of the blade (11), and the low pressure introduction passage (19) is connected to the back pressure space (1
You will face 2). By this, the suction path (5a)
The low pressure inside passes through the low pressure introduction path (19) and the back pressure space (12).
The pressure applied to the back surface (11a) of the blade (11) becomes low pressure.

In this way, even in this modification, the pressure acting on the back surface (11a) of the blade (11) can be switched according to the rotation state of the roller (6), so that the blade (11) Mechanical loss due to sliding between the tip surface and the outer peripheral surface of the roller (6) can be significantly reduced. Further, in the configuration of this modification, the pressure introducing passage (17) and the recessed portion (11e) of the blade right side surface (11c), which are required in the configuration of the first embodiment, are not required, so that the configuration can be simplified. Not only that, the rigidity of the blade (11) is improved, and its life can be extended.

(Second Embodiment) Next, a second embodiment according to the invention described in claim 3 will be described. This example is also a modified example of the blade (11) and the blade peripheral structure, and since the other configurations are similar to those of the above-described first example,
The description will be omitted, and only the characteristic configuration of this example will be described.

As shown in FIG. 7, the blade (1
1) and its surrounding structure, the high pressure introduction passage (1
8) and the high-pressure introducing space (15) are configured in the same manner as in the first embodiment described above, and do not include the low-pressure introducing passage (19). Further, the pressure introducing passage (17) is composed of only the above-mentioned first passage (17a), and is not provided with the above-mentioned second passage (17b). A low pressure introduction passage (21) is formed on the right side surface (11c) of the blade (11). This low pressure introduction path (2
1) is a groove formed on the right side surface (11c) of the blade (11), the front end position of which is the first passage (1).
7a) is set slightly forward (downward in FIG. 7) from the position where the rear end of the blade (11) is located (1).
It is open to 1a). In addition, this low pressure introduction path (2
As shown in FIG. 7, the front end position of 1) is set so that the front end portion of the roller (6) faces the low pressure chamber (9a) only when the roller (6) is at the bottom dead center.

When the compressor of this example is driven,
When the roller (6) is at the top dead center, the low pressure introduction path (2
The high-pressure introduction passage (18) communicates with the high-pressure introduction space (15) without exposing the low-pressure chamber (9a) to the high-pressure introduction passage (1).
8), the high pressure introducing space (15), the pressure introducing passage (17) and the low pressure introducing passage (21), and is introduced into the back pressure space (12). On the other hand, as shown in FIG. 7, when the roller (6) is at the bottom dead center, the high pressure introduction passage (18)
The opening at one end of is closed by the left side surface (11b) of the blade (11), and the front end portion of the low pressure introduction passage (21) faces the low pressure chamber (9a). As a result, the low pressure in the low pressure chamber (9a) is introduced into the back pressure space (12) via the low pressure introduction passage (21).

As described above, even in the structure of this embodiment, the back surface (1) of the blade (11) is changed depending on the rotation state of the roller (6).
Since the pressure acting on 1a) can be switched, mechanical loss due to sliding between the tip surface of the blade (11) and the outer peripheral surface of the roller (6) can be significantly reduced. Further, in the configuration of the present example, the second passage (17b) and the low-pressure introduction passage (19), which are required in the configuration of the first embodiment, are unnecessary, so that the configuration can be simplified.

Although the above-described 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.

[0039]

As described above, according to the present invention, the following effects are exhibited. According to the invention described in claim 1, the blade (1
The fluid pressure acting on the back surface (11a) of 1) is switched between high pressure and low pressure, and at least in the top dead center state of the roller (6), the high pressure acts on the back surface (11a) and at least the bottom death of the roller (6). In the point state, the back surface (11a) is provided with the fluid pressure switching means (20) for exerting a low pressure, so that the blade (1) near the bottom dead center of the roller (6).
The pressing force on the outer peripheral surface of the roller (6) of 1) can be set low,
By preventing the blade (11) from separating from the roller (6) over the entire rotation of the roller (6), the tip surface of the blade (11) slides on the outer peripheral surface of the roller (6). The mechanical loss can be reduced and the compressor efficiency can be improved. Further, since the pressing force of the blade (11) that acts in the direction of impeding the rotation of the roller (6) from the bottom dead center state to the top dead center state is set low,
The roller (6) can be smoothly rotated.

According to the second aspect of the present invention, the high-pressure introducing passage (18) for introducing the fluid pressure switching means (20) into the back pressure space (12) with the fluid pressure in the casing inner space (2a).
And a low pressure introduction passage (19) for introducing the fluid pressure of the suction passage (5a) into the back pressure space (12), the high pressure and the low pressure introduced into the back pressure space (12). And the average value of the pressing force of the blade (11) can be significantly reduced, and the compressor efficiency can be significantly improved.

According to the third aspect of the present invention, the fluid pressure switching means (20) introduces the fluid pressure in the casing internal space (2a) into the back pressure space (12).
And a low pressure introduction passage (21) for introducing the fluid pressure of the low pressure chamber (9a) into the back pressure space (12), so that a passage for low pressure introduction is formed in the cylinder (5). It is not necessary to do so, and the introduction of low pressure can be performed with a simple structure.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a rolling piston type compressor according to a first embodiment.

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

FIG. 3 is a diagram showing a blade.

FIG. 4 is a cross-sectional view of the periphery of the blade in a state where the roller is at top dead center.

FIG. 5 is a cross-sectional view of the periphery of the blade in a state where the roller is at the bottom dead center.

FIG. 6 is a view corresponding to FIGS. 4 and 5 showing a modification of the first embodiment.

FIG. 7 is a view corresponding to FIG. 5 in the second embodiment.

FIG. 8 is a view corresponding to FIG. 2 in a conventional rolling piston type compressor.

[Explanation of symbols]

 (1) Rolling piston type compressor (2) Casing (3) Drive means (3b) Crankshaft (drive shaft) (3f) Cam part (eccentric part) (4) Compressor body (compression means) (5) Cylinder ( 5a) Suction path (5b) Blade groove (5d) Discharge path (6) Roller (7) Front head (head part) (8) Rear head (head part) (9) Compression chamber (9a) Low pressure chamber (9b) High pressure chamber (11) Blade (11a) Back surface (12) Back pressure space (16) Low pressure introduction space (18) High pressure introduction passage (19) Low pressure introduction passage (20) Fluid pressure switching means (21) Low pressure introduction passage

Claims (3)

[Claims] 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 (3f) 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 to the cylinder (5) so that 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 applied to the back surface (11a) of the rotor (6). ), The compression chamber (9) is divided into a low pressure chamber (9a) and a high pressure chamber (9b), and the compression chamber (9) has a fluid suction path (5a) and The discharge passage (5d) is connected, and the roller (6) rotates in the cylinder (5) as the driving means (3) is driven, and the suction passage (5a) to the compression chamber (9). In a rolling piston compressor configured to draw fluid into and compress the fluid. The blade according to the rotational position of the roller (6) (1
The fluid pressure acting on the back surface (11a) of 1) is switched between high pressure and low pressure, and at least in the top dead center state of the roller (6), the high pressure acts on the back surface (11a) and at least under the roller (6). A rolling piston type compressor characterized in that a fluid pressure switching means (20) for applying a low pressure is provided on the rear surface (11a) in a dead center state. 2. The rolling piston type compressor according to claim 1, wherein the blade (11) is inserted into a blade groove (5b) formed in the cylinder (5), and the blade groove (5b) and the blade (5b). 11) rear surface (11a)
A back pressure space (12) is formed between the back pressure space and the back pressure space (12), and the fluid pressure switching means (20) introduces the fluid pressure in the casing inner space (2a) into the back pressure space (12).
8) and the fluid pressure in the suction passage (5a) to the back pressure space (12).
And a low pressure introducing passage (19) for introducing into the rolling piston type compressor. 3. The rolling piston type compressor according to claim 1, wherein the blade (11) is inserted into a blade groove (5b) formed in the cylinder (5), and the blade groove (5b) and the blade (5b). 11) rear surface (11a)
A back pressure space (12) is formed between the back pressure space and the back pressure space (12), and the fluid pressure switching means (20) introduces the fluid pressure in the casing inner space (2a) into the back pressure space (12).
8) and the fluid pressure in the low-pressure chamber (9a) to the back pressure space (12).
And a low pressure introducing passage (21) for introducing into the rolling piston type compressor.