JP2576235B2 - Rotary compressor - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a rotary compressor, and more particularly to a measure for simplifying a discharge valve mechanism on a compressed fluid discharge side.

(Prior Art) Until now, as an example of a rotary compressor provided in a refrigerant circuit of a refrigerator or used as a vacuum pump or the like, "JIS Industrial Terminology Dictionary" (P.1239) and FIG. Are configured as shown in FIG. According to this, a cylinder suction passage (d) for connecting a compression chamber and a suction-side fluid chamber inside the cylinder (a) to a cylindrical cylinder (a), and a communication between the compression chamber and the discharge-side fluid chamber. A cylinder discharge path (e) is formed. A cylindrical blade shoe insertion hole (f) is formed near the cylinder suction passage (d) and the cylinder discharge passage (e), and the blade shoe insertion hole is formed in the blade shoe insertion hole (f). A blade shoe (g) having the same shape as (f) is rotatably fitted. Also, this blade shoe (g)
A blade insertion hole (h), which is a through hole extending in the radial direction, is formed in the center of the blade insertion hole (h).
The rotary piston (i) is disposed so as to be eccentric with respect to the center of the cylinder and a part of the outer peripheral surface thereof is in contact with the inner peripheral surface of the cylinder (a). The blade (j) is integrally formed, and the blade (j) is slidably inserted into the blade insertion hole (h). It is divided into a low-pressure side compression chamber (b) opening d) and a high-pressure side compression chamber (c) opening a cylinder discharge passage (e). Further, the cylinder discharge passage (e) is provided with a reed valve (k) made of a thin metal plate which is opened toward the discharge-side fluid chamber by high pressure in the high-pressure side compression chamber (c). When the compressor is driven, the fluid sucked into the low-pressure side compression chamber (b) from the suction-side fluid chamber via the cylinder suction path (d) is rotated by the rotation of the rotary piston (i). Compression chamber (b)
Becomes a high-pressure side compression chamber (c), and in the high-pressure side compression chamber (c), its volume is reduced to a high pressure, and this fluid pressure pushes the reed valve (k) toward the discharge side fluid chamber. The high-pressure fluid is discharged from the cylinder discharge passage (e) to the discharge-side fluid chamber.

(Problems to be Solved by the Invention) However, such a compressor having a reed valve disposed on the discharge side of the fluid has the following problems.

(I) The reed valve is made of a thin metal plate having insufficient strength, and may be damaged if the valve is opened and closed for a long period of time because the valve is closed and collides with a valve seat. When such damage (break) occurs, the fluid in the high-pressure side compression chamber leaks from the damaged portion to the discharge-side fluid chamber, and the fluid cannot be brought into a predetermined high-pressure state in the high-pressure side compression chamber. This leads to a reduction in compressor efficiency.

(Ii) If the fluid pressure in the high-pressure side compression chamber does not exceed a predetermined value, the reed valve does not perform its opening operation, and in the compression stroke of the fluid, after the fluid pressure reaches the predetermined value, the reed valve operates at that pressure. The pressure in the high-pressure side compression chamber may be higher than necessary, i.e., in an over-compressed state, between the time when the predetermined pressure value is reached and the time when the reed valve is opened. When such an over-compression state occurs, not only a desired high-temperature and high-pressure fluid cannot be obtained, but also a driving force loss occurs and the compressor efficiency is reduced. Also,
In order to avoid such an overcompression state, high precision is required for the dimensions and shape of the reed valve, which has led to an increase in manufacturing costs.

(Iii) As described above, the reed valve sits on the valve seat at the time of the closing operation. At that time, the reed valve collides with the valve seat, so that noise due to the collision sound is generated.

To solve these problems, instead of a reed valve,
It is conceivable to newly provide a valve mechanism that opens and closes with a mechanical driving force, but in the case of such a configuration,
As the structure becomes more complicated, the number of failure factors increases, so that the reliability of the compressor is reduced and the production cost is increased. Further, it is conceivable that the increase in the number of drive units causes generation of new noise and vibration, and loss of the rotational driving force of the rotary piston due to valve driving, which causes a decrease in compressor efficiency. Therefore, an object of the present invention is to improve a discharge-side valve mechanism and to obtain a rotary-type compressor which can solve the above-mentioned problems at once with a simple configuration.

(Means for Solving the Problems) In order to achieve the above object, the present invention eliminates the reed valve by providing a sliding valve mechanism in the discharge side valve mechanism. As a specific means, the invention described in claim (1), as shown in FIG.
In the cylinder (3), a rotary piston (5) integrally formed with a blade (52) is disposed eccentrically from the center of the cylinder (3) so that the inside of the cylinder (3) is connected to a low pressure side space. It is assumed that the rotary compressor is partitioned into a side compression chamber (21) and a high pressure side compression chamber (22) connected to the high pressure side space (7). A cylinder discharge passage having a blade shoe insertion hole (32) formed in the cylinder (3), one end communicating with the blade shoe insertion hole (32), and the other end communicating with the high pressure side space (7). (33) is provided. The blade shoe (4) is rotatably fitted into the blade shoe fitting hole (32), and the blade (52) of the rotary piston (5) is provided on the blade shoe (4). Blade insertion hole (4
Insert it slidably through 1). The blade shoe (4) has one end communicating with the blade insertion hole (41) and the other end communicating with the cylinder discharge path (33) within a predetermined rotation range of the blade shoe (4). 42) is provided. Further, one end of the blade (52) is always in communication with the high pressure side compression chamber (22), and the other end of the blade (52) is at a predetermined sliding position between the blade (52) and the blade shoe (4). A blade discharge path (53) communicating with (42) is formed. Then, each of the discharge paths (33),
The opening position of (42), (53) is adjusted to the high pressure side compression chamber (22)
One end of the cylinder discharge path (33) and the other end of the blade shoe discharge path (42) communicate with each other within a predetermined rotation range from a predetermined rotation angle position of the rotary piston (5) in which the fluid in the inside becomes a high pressure state, and The configuration is such that one end of the blade shoe discharge path (42) communicates with the other end of the blade discharge path (53).

Further, according to the invention described in claim (2), as shown in FIGS. 3 (e) and (a), the rotary compressor according to claim (1) has three discharge paths (33), ( 42),
(53), the communication start point between the blade shoe discharge path (42) and the blade discharge path (53) regulates the start of fluid discharge to the high pressure side space (7), and the cylinder discharge path (33) and the blade shoe discharge The end point of communication with the road (42) is set so as to regulate the end of discharge of the fluid to the high-pressure side space (7).

(Operation) The operation of the present invention with the above configuration will be described below.

In the invention described in claim (1), the fluid is sucked from the low-pressure side space into the low-pressure side compression chamber (21), and the volume of the high-pressure side compression chamber (22) is reduced by the rotation of the rotary piston (5). Compress. During the discharge operation of the compressed fluid, each of the discharge paths (33), (42), and (42) at a predetermined rotation angle position of the rotary piston (5) at which the fluid in the high-pressure side compression chamber (22) is in a high pressure state. The fluid in the high-pressure side compression chamber (22) flows through each discharge path (5
The liquid is discharged from the cylinder (3) to the high-pressure side space (7) through (3), (42), and (33). That is, each discharge path (53), (4
The mechanism as a discharge valve is exhibited by switching between the communicating state and the non-communicating state of 2) and (33), and thus, with a simple configuration, low noise and high reliability without using a reed valve. A discharge valve mechanism is obtained.

In the invention described in claim (2), the cylinder discharge path (33) and the blade shoe discharge path are controlled such that the communication start point between the blade shoe discharge path (42) and the blade discharge path (53) regulates the start of discharge. By setting the communication end point with (42) so as to regulate the discharge end, the discharge start timing and discharge end timing of the fluid from the high-pressure side compression chamber (22) can be set optimally. The operation is performed accurately, and the setting can be easily performed.

Example Next, an example of the present invention will be described with reference to the drawings.

FIG. 1 is a cross-sectional view around a compression chamber (2) in a rotary compressor (1) provided in a refrigerant circuit of an air conditioner. As shown in this figure, the periphery of the compression chamber (2) of the rotary compressor (1) in the present example is constituted mainly by a cylinder (3), a blade shoe (4) and a rotary piston (5). .

The cylinder (3) is a cylindrical member, the outer peripheral surface of which is fixedly supported on the inner surface of a compressor casing (not shown), while the interior thereof is shown on both upper and lower end surfaces of the cylinder (3). The compression chamber (2) as a low columnar space is formed by attaching a flat disk-shaped side case that is not used. The cylinder (3) has a cylinder suction passage (31) communicating the compression chamber (2) and a suction pipe (6) connected to the cylinder (3) and having one end connected to the low-pressure side space.
Are drilled. Further, at a position close to the cylinder suction passage (31), a substantially cylindrical blade shoe insertion hole (32) is provided.
Are formed. The blade shoe insertion hole (32) is penetrated in the axial direction of the cylinder (3), and has a diameter substantially equal to the thickness of the cylinder (3). By arranging the side cases on the upper and lower surfaces, a space for supporting the blade shoe (4) is formed. A characteristic portion of the cylinder (3) is a cylinder discharge passage (33) that connects the blade shoe insertion hole (32) with the high-pressure space (7) outside the cylinder (3). The cylinder discharge passage (33) extends from the outer peripheral surface of the cylinder (3) to the inner surface of the blade shoe insertion hole (32), and has a smaller diameter than the cylinder suction passage (31). At the same time, the direction is substantially perpendicular to the extension direction of the cylinder suction hole (31).

The blade shoe (4) is formed in a shape substantially matching the cylindrical shape of the blade shoe insertion hole (32),
The blade shoe is inserted into the hole (32), and is rotatable in the blade shoe insertion hole (32). A blade insertion hole (41) extending in the radial direction of the blade shoe (4) and penetrating the blade shoe (4) is formed at a substantially central portion in the horizontal direction. A characteristic part of the blade shoe (4) is a blade shoe discharge path (42) formed between the blade insertion hole (41) and the outer surface of the blade shoe (4). This blade shoe discharge path (42)
Is a through hole having substantially the same diameter as the cylinder discharge path (33), extending in a direction perpendicular to the direction in which the blade insertion hole (41) extends, and perpendicular to the direction in which the blade insertion hole (41) extends. Compression chamber (2) with respect to the center line of the
It is formed at a position slightly shifted to the side. For more information,
When the rotatable blade shoe (4) slightly rotates clockwise beyond the rotation angle of the rotary piston exceeding 180 ° (the state shown in FIG. 3 (d)), the cylinder discharge path (33) and the blade shoe are rotated. The rotary piston (5) rotates so that the discharge path (42) communicates with the discharge path (42). When the rotation angle reaches 0 °, the communication between the two paths (33) and (42) is interrupted. The opening position is set. That is, as shown in FIGS. 3 (d) to 3 (a), the blade shoe (4) is displaced in the clockwise direction until the rotation angle of the rotary piston (5) exceeds 180 ° and reaches 360 °. The cylinder discharge path (33) and the blade shoe discharge path (42) are set so as to communicate with each other.

The rotary piston (5) is a cylindrical piston body (5
A blade (52) is connected to 1). The piston body (51) has a low cylindrical shape, and both upper and lower end surfaces thereof are in contact with the side case while maintaining airtightness. A crankshaft (not shown) extending from a drive system of the compressor is inserted into the piston body (51).
The center of the crankshaft (O1) passing through the center of the cylinder and the center of the cam portion (O2) as an insertion part of the crankshaft are eccentric by a predetermined dimension, so that the center of the cylinder and the center of the rotary piston also have a predetermined amount. Have eccentricity. Therefore, the outer peripheral surface of the piston body (51) and the cylinder (3)
There is a slight gap between the inner peripheral surface and the inner peripheral surface to maintain airtightness, and separates the high-pressure chamber from the low-pressure chamber. The blade (52) extends in the radial direction from the outer surface of the piston body (51) to extend the blade shoe (4).
Is slidably inserted into the blade insertion hole (41).
Therefore, the inside of the compression chamber (2) is divided into two chambers of a low pressure side compression chamber (21) and a high pressure side compression chamber (22) by the rotary piston (5) composed of the piston body (51) and the blade (52). I have. A characteristic portion of the rotary piston (5) is a blade discharge path (53) provided in the blade (52). As shown in FIG. 2, the blade discharge path (53) is provided on the side of the blade (52) facing the high-pressure side compression chamber (22).
It is formed in a rectangular groove extending in the direction of the blade tip with a predetermined width from the connection portion with the compression chamber (1), and its upper end position is, as shown in FIGS. ) Communicates when the rotation angle of the rotary piston (5) reaches a preset predetermined pressure exceeds 225 °, and when it reaches 135 °, communication between the blade shoe discharge path (42) and the blade discharge path (53). Is set to block.

Thus, the communication between the cylinder discharge passage (33) and the blade shoe discharge passage (42) is performed until the rotation angle of the rotary piston (5) exceeds 180 ° and reaches 360 °,
On the other hand, the communication between the blade shoe discharge path (42) and the blade discharge path (53) depends on the rotation angle of the rotary piston (5).
The opening positions of the discharge paths (33), (42), and (53) are set so as to be performed between 225 ° and 135 °.

Next, when the rotary partition compressor is driven, a third
Description will be made with reference to the drawings.

First, FIG. 3 (a) (rotation angle 0 of rotary piston)
When the rotary piston (5) starts to rotate from the state of ゜), the refrigerant previously sucked into the compression chamber (2) from the cylinder suction passage (31) in the previous stroke starts to be compressed. In this state, the communication state of each of the discharge paths (33), (42), and (53) is such that the blade shoe discharge path (42) and the blade discharge path (53) are in communication, but the cylinder discharge path (33). ) And the blade shoe discharge path (42) are not in communication with each other, so that the internal space (7) of the casing of the compressor and the compression chamber (2) are not provided.
Is not communicated with.

In the state shown in FIG. 3 (b) at a rotation angle of the rotary piston of 80 °, the blade shoe (4) is displaced in the counterclockwise rotation direction, so that the cylinder discharge path (33) and the blade shoe discharge path are still present. (42) is in a non-communication state, and the casing internal space (7) and the high-pressure side compression chamber (22) are not in communication with each other as in the state of FIG. 3 (a). In the low-pressure side compression chamber (21), a refrigerant suction operation for compressing in the next stroke is performed.

In the state shown in FIG. 3C at a rotation angle of 135 ° of the rotary piston, the blade shoe discharge path (42) and the blade discharge path (53) are also in a non-communication state, and each discharge path (3
3), (42) and (53) compress the refrigerant in the high-pressure side compression chamber (22) in a non-communicating state.

In the state shown in FIG. 3 (d) with a rotation angle of 180 °,
When the rotary piston (5) has reached the lowest point, the blade shoe (4) returns to the state shown in FIG. 3 (a), while the blade (52) moves into the compression chamber (2). It is in the maximum protruding state. Also in this case, each discharge path (3
3), (42), and (53) are not communicated, and the refrigerant in the compression chamber on the high pressure side is compressed. In rotation after this rotation angle of 180 °, the blade shoe (4) is displaced clockwise, so that the cylinder discharge path (33) and the blade shoe discharge path (42) are communicated.

Then, in the state of FIG. 3 (e) at a rotation angle of 225 °, the refrigerant in the high pressure side compression chamber (22) reaches a predetermined pressure. In rotation after this state, the blade discharge path (53) and the blade shoe discharge path (42) are in communication with each other, and the refrigerant in the high-pressure side compression chamber (22) passes through the blade discharge path (5).
From 3), the oil is discharged into the casing internal space (7) through the blade shoe discharge path (42) and the cylinder discharge path (33).

The state shown in FIG. 3 (f) is a state in which the opening positions of the cylinder discharge path (33) and the blade shoe discharge path (42) match, that is, three discharge paths (33), (42), (53)
Are in a state of communicating at the same time, and a state in which the refrigerant discharge passage has a maximum diameter. Thereafter, the rotation of the rotary piston (5) proceeds, and when the rotation angle reaches 360 °, the third rotation is performed.
Returning to the state shown in FIG. 9A, the above-described process is repeated.

As described above, the refrigerant discharge angle in this example is the rotation angle (180 ° to 360 °) of the rotary piston and the blade shoe discharge path (42) that connect the cylinder discharge path (33) and the blade shoe discharge path (42). The rotation angle of the rotary piston (225 ° to 135
The high-pressure side compression chamber (22) and the casing internal space (7) are communicated only at a rotation angle of 225 ° to 360 ° as the wrap portion of (1), and the compressed refrigerant is discharged.

Thus, according to the present invention, each of the discharge paths (53), (4
2) and (33) are switched between the communicating state and the non-communicating state, so that the mechanism as a discharge valve is exhibited. By eliminating the conventional reed valve, noise is reduced and damage-causing parts are reduced. Further, since the high-pressure side compression chamber (22) and the casing internal space (7) are forcibly communicated with each other, there is no occurrence of the conventional over-compression state of the refrigerant. Further, a stable valve opening operation can be obtained with a simple configuration without requiring a mechanical driving force means. Further, the communication state of each discharge path is closed when the rotation angle of the rotary piston reaches 360 °, so that the refrigerant discharged into the casing internal space does not flow back to the high-pressure side compression chamber. Further, the start of communication of the three discharge paths (33), (42), and (53) is regulated between the blade shoe discharge path (42) and the blade discharge path (53), while the end of communication is determined by the cylinder discharge path. (3
By regulating between 3) and the blade shoe discharge path (42), the communication operation is performed accurately, and the setting is easily performed.

In the present embodiment, the rotation angle of the rotary piston (5) through which the discharge passages (33), (42) and (53) communicate simultaneously is set to 225 ° to 360 °, but the communication start angle can be set as appropriate. is there. Further, the present invention is not limited to the compressor in the air conditioner as in the present embodiment, and can be applied to various fluid devices such as a vacuum pump.

(Effects of the Invention) As described above, according to the present invention, the following effects are exhibited.

In the invention described in claim (1), the fluid in the high-pressure side compression chamber is discharged at the predetermined rotation angle position of the rotary piston at which the fluid in the high-pressure side compression chamber communicates at the same time, so that the fluid in the high-pressure side compression chamber is discharged. Is discharged. This allows
The conventional reed valve can be eliminated, noise is reduced, and the cause of damage is reduced.Furthermore, the fluid does not become overcompressed in the high-pressure side compression chamber, and vibration noise is generated. It is possible to obtain a highly reliable valve mechanism of a rotary compressor that performs a stable valve opening operation with a simple configuration without using a mechanical valve mechanism that is easy and causes a production cost and a driving force loss.

In the invention described in claim (2), the communication end point between the cylinder discharge path and the blade shoe discharge path regulates the discharge end so that the communication start point between the blade shoe discharge path and the blade discharge path controls the discharge start. The communication operation is performed accurately, and the setting can be easily performed. Further, as in the above-described embodiment, the rotation angle of the
If the position of ゜ is the final point, the fluid discharged to the discharge-side fluid chamber does not flow back to the high-pressure side compression chamber, so that the compression efficiency can be improved.

[Brief description of the drawings]

1 to 3 show an embodiment of the present invention. FIG. 1 is a cross-sectional view showing a structure around a compression chamber of a compressor, FIG. 2 is a perspective view around a blade discharge path, and FIG. FIG. 3 is a diagram corresponding to FIG. 1 for explaining a communication state of each discharge path accompanying rotation of a rotary piston. FIG. 4 is a diagram corresponding to FIG. 1 in a conventional compressor. (1) ... rotary compressor, (21) ... low-pressure side compression chamber, (22) ... high-pressure side compression chamber, (3) ... cylinder,
(32) ... blade shoe insertion hole, (33) ... cylinder discharge path, (4) ... blade shoe, (41) ... blade insertion hole, (42) ... blade shoe discharge path, (5) ...
… Rotary piston, (52) …… Blade, (53) ……
Blade discharge path.

Claims (2)

(57) [Claims] A rotary piston (5) integrally formed with a blade (52) is disposed eccentrically from the center of the cylinder (3) so that the inside of the cylinder (3) has a low pressure side. A rotary-type compressor partitioned into a low-pressure side compression chamber (21) connected to a space and a high-pressure side compression chamber (22) connected to a high-pressure side space (7); Shoe fitting hole (32)
And a cylinder discharge path (33) having one end communicating with the blade shoe fitting hole (32) and the other end communicating with the high pressure side space (7). A blade shoe (4) is rotatably fitted in 32), and a blade (52) of a rotary piston (5) is fitted in the blade shoe (4).
Is slidably inserted into a blade insertion hole (41) provided in the blade shoe (4). One end of the blade shoe (4) communicates with the blade insertion hole (41), and the other end of the blade shoe (4) has the other end. A blade shoe discharge path (42) communicating with the cylinder discharge path (33) is provided in a predetermined rotation range of the blade shoe (4). One end of the blade (52) has a high-pressure side compression chamber (22). )
A blade discharge path (53) is formed, the other end of which is in communication with the blade shoe discharge path (42) at a predetermined sliding position between the blade (52) and the blade shoe (4); The opening position of each of the discharge passages (33), (42) and (53) is within a predetermined rotation range from a predetermined rotation angle position of the rotary piston (5) where the fluid in the high-pressure side compression chamber (22) is in a high pressure state. , One end of the cylinder discharge path (33) communicates with the other end of the blade shoe discharge path (42), and one end of the blade shoe discharge path (42) and the other end path (53) of the blade discharge path (53). Characterized in that it is set so as to communicate with the other end of the rotary compressor. 2. The rotary compressor according to claim 1, wherein the three discharge paths (33), (42) and (53) are a blade shoe discharge path (42) and a blade discharge path (53). The start point of communication with the cylinder regulates the start of fluid discharge into the high pressure side space (7), and the cylinder discharge path (33) and the blade shoe discharge path (4
A rotary compressor characterized in that the end point of communication with 2) is set so as to regulate the end of discharge of fluid to the high pressure side space (7).