JP2006132347A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor capable of taking a large suction sectional area in designing and capable of preventing the suction sectional area from being reduced, a suction resistance from being increased, and a suction amount from being decreased during a suction process. <P>SOLUTION: This compressor C comprises a compression element 3 formed of a cylinder 8 in which a compression space 21 is formed, a drive element 2 driving the compression element 3, a rotating shaft 5 for transmitting the rotating force of the drive element 2 to the compression element 3, a suction port 27 and a discharge port 28 communicating with the compression space 21 in the cylinder 8, a compression member 9 having a tilted one surface with a thick wall part 31 and a thin wall part 32 continuously connected to each other, disposed in the cylinder 8 and rotated, and compressing a fluid sucked from the suction port 27 into the compression space 21 and discharging it from the discharge port 28, and a vane 11 disposed between the suction port 27 and the discharge port 28, brought into contact with the one surface of the compression member 9, and dividing the compression space 21 in the cylinder 8 into a low pressure chamber LR and a high pressure chamber HR. The suction port 27 is so disposed that the fluid sucked from the suction port 27 into the compression space 21 flows to the upper surface 33 of the compression member 9. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a compressor that compresses a fluid such as refrigerant or air sucked from a suction port and discharges the fluid from a discharge port.

2. Description of the Related Art Conventionally, a method has been proposed in which a swash plate that rotates in a cylinder is provided, and a compression space formed above and below the swash plate is partitioned by vanes to compress fluid (for example, see Patent Document 1). This type of compressor has the advantage of relatively simple structure and low vibration, but the high-pressure chamber and low-pressure chamber are adjacent to each other above and below the swash plate in the entire area of the cylinder. There was a problem to do.
The present inventors have previously proposed a compressor that solves this problem, further simplifies the structure, reduces torque fluctuation, and has high efficiency (see Patent Document 2).
Special table 2003-532008 gazette Japanese Patent Application No. 2004-003142

FIG. 7 is a longitudinal side view of a conventional compressor C, and FIG. 8 is a plan vertical view of the compressor C. 7 and 8, the same reference numerals as those in FIGS. 1 to 6 showing the embodiments of the present invention to be described later have the same or similar functions.
As shown in FIGS. 7 and 8, the compressor C previously proposed by the present inventors is a suction pipe for sucking fluid in a refrigerant circuit (not shown) outside the system into the compression space 21 of the cylinder 8. 26 and a suction passage 24 are formed on the side surface of the cylinder 8, and the fluid flows substantially perpendicularly to the axial direction of the rotary shaft 5 through the suction pipe 26 and the suction passage 24 and enters the compression space 21 from the side surface of the cylinder 8. Since the suction port 27 is provided so as to flow, the suction sectional area cannot be increased at the time of design, and the suction sectional area decreases due to the influence of the side surface 35 of the compression member 9 that rotates during the suction process. However, there is a problem that the performance of the compressor is deteriorated due to a decrease in the suction amount.

  The purpose of the present invention is to solve the conventional problems and to increase the suction sectional area at the time of design, and to prevent the reduction of the suction sectional area, the suction resistance and the suction amount during the suction process. Is to provide.

The compressor according to claim 1 of the present invention for solving the above problem is
A compression element composed of a cylinder having a compression space therein;
A driving element for driving the compression element; and a rotating shaft for transmitting a rotational force of the driving element to the compression element;
A suction port and a discharge port communicating with the compression space in the cylinder;
One surface is inclined with a continuous thick portion and thin portion, and is disposed in the cylinder and rotates, compresses the fluid sucked into the compression space from the suction port, and discharges it from the discharge port. A compression member;
A compressor provided with a vane disposed between the suction port and the discharge port, abutting against one surface of the compression member, and dividing the compression space in the cylinder into a low pressure chamber and a high pressure chamber;
The suction port is arranged so that the fluid sucked into the compression space from the suction port flows toward the upper surface of the compression member.

  The compressor according to claim 2 of the present invention is the compressor according to claim 1, wherein the compression element includes a support member that has a main bearing of the rotating shaft and closes an opening of the cylinder. The cylinder has a sub-bearing of the rotating shaft located on the opposite side of the support member, and forms a suction passage for sucking fluid in a refrigerant circuit in the support member, and the suction passage through the suction passage. The fluid is sucked into the compression space from the port.

According to a first aspect of the present invention, there is provided a compressor according to a first aspect of the present invention, a compression element comprising a cylinder having a compression space therein, a drive element that drives the compression element, and a rotational force of the drive element to the compression element. It has a rotating shaft for transmission, a suction port and a discharge port communicating with the compression space in the cylinder, a continuous thick portion and a thin portion, and one surface is inclined and arranged and rotated in the cylinder. A compression member that compresses the fluid sucked into the compression space from the suction port and discharges the fluid from the discharge port; and is disposed between the suction port and the discharge port and contacts one surface of the compression member; A compressor provided with a vane that divides an inner compression space into a low-pressure chamber and a high-pressure chamber,
The suction port is arranged so that the fluid sucked into the compression space from the suction port flows toward the upper surface of the compression member, and while being a small and simple structure, High pressure and low pressure are no longer adjacent to each other in the entire area of the cylinder as in the prior art, and the seal dimension between the cylinder and the thick part that will correspond to the high pressure chamber can be secured, and the occurrence of refrigerant leakage can be prevented. Efficient operation is possible, and the thick part of the compression member acts as a flywheel, reducing torque fluctuations.
Since the suction port is disposed so that the fluid flows toward the upper surface of the compression member, it is possible to increase the suction cross-sectional area at the time of design, and the influence of the side surface of the compression member that rotates during the suction process This reduces the suction cross-sectional area during the suction process, increases the suction resistance, and reduces the suction amount, and has a remarkable effect that the performance can be improved.

The compressor according to claim 2 of the present invention is the compressor according to claim 1, wherein the compression element includes a support member that has a main bearing of the rotating shaft and closes an opening of the cylinder. The cylinder has a sub-bearing of the rotating shaft located on the opposite side of the support member, and forms a suction passage for sucking fluid in a refrigerant circuit in the support member, and the suction passage through the suction passage. It is characterized by sucking fluid into the compression space from the port, and it becomes unnecessary to separately provide a support member for the auxiliary bearing of the rotating shaft, and it is possible to reduce the number of parts and further reduce the size,
Since the suction port can be easily disposed so that the fluid flows toward the upper surface of the compression member, there is a further remarkable effect that the performance can be reliably improved.

Next, the present invention will be described in detail based on embodiments with reference to the drawings.
In addition, the compressor C of the Example demonstrated hereafter comprises the refrigerant circuit of a refrigerator, for example, plays the role which sucks in and compresses a refrigerant | coolant and discharges it in a circuit.
(First embodiment of the present invention)
FIG. 1 is a longitudinal side view for explaining an example of the compressor C of the present invention, FIG. 2 is another longitudinal side view of the compressor C of the present invention, and FIG. 3 is a plan longitudinal view of the compressor C of the present invention. 4 is a perspective view of a part of the compression element 3 of the compressor C of the present invention, and FIG. 5 is a side view of the rotary shaft 5 including the compression member 9.

  In FIGS. 1 and 2, reference numeral 1 denotes an airtight container. The airtight container 1 accommodates a driving element 2 on the upper side and a compression element 3 driven by the driving element 2 on the lower side.

  The drive element 2 is an electric motor that is fixed to the inner wall of the hermetic container 1 and includes a stator 4 around which a stator coil is wound, and a rotor 6 having a rotation shaft 5 at the center inside the stator 4. A gap 10 is formed between the outer peripheral portion of the stator 4 of the driving element 2 and the sealed container 1 so as to communicate with the upper and lower portions.

  The compression element 3 includes a support member 7 fixed to the inner wall of the hermetic container 1, a cylinder 8 attached to the lower surface of the support member 7 with bolts, and a compression member 9 (hereinafter referred to as a swash 9) disposed in the cylinder 8. In some cases, the vane 11 and a discharge valve (not shown). The central portion of the upper surface of the support member 7 projects upward concentrically, and the main bearing 13 of the rotating shaft 5 is formed there, the central portion of the lower surface projects downward concentrically, and the lower surface 14A of the projection 14 is smooth. It is considered as a surface.

  As shown in FIG. 2, a slot 16 is formed in the protrusion 14 of the support member 7, and the vane 11 is inserted into the slot 16 so as to be able to reciprocate up and down. A back pressure chamber 17 for applying the high pressure in the sealed container 1 as a back pressure to the vane 11 is formed in the upper portion of the slot 16, and an urging force for pressing the upper surface of the vane 11 downward in the slot 16 is formed. A coil spring 18 is disposed as a means.

A central portion of the cylinder 8 is recessed downward, and a compression space 21 is formed in the recessed portion 19. An auxiliary bearing 22 is formed in the center of the lower surface of the recessed portion 19 of the cylinder 8.
As shown in FIG. 1, a suction passage 24 is formed in the support member 7, and a suction pipe 26 is attached to the sealed container 1 and connected to the suction passage 24. A suction port 27 that communicates with the compression space 21 is formed in the protrusion 14 of the support member 7, and the suction port 27 communicates with the suction passage 24 and is sucked into the compression space 21 from the suction port 27. A suction port 27 is provided so that the refrigerant flows toward the upper surface 33 of the swash 9.
As shown in FIG. 3, a discharge port 28 is formed in the cylinder 8, and the discharge port 28 communicates with the inside of the sealed container 1 on the side surface of the cylinder 8. The vane 11 is located between the suction port 27 and the discharge port 28.

  The rotary shaft 5 is inserted through the central portion of the support member 7 and the cylinder 8, and the central portion in the vertical direction is rotatably supported by the main bearing 13, and the lower end is rotatably supported by the auxiliary bearing 22. The swash 9 is formed integrally with the lower portion of the rotating shaft 5 and is disposed in the recessed portion 19 of the cylinder 8.

  As shown in FIG. 5, the swash 9 has a substantially cylindrical shape concentric with the rotary shaft 5 as a whole, and has a shape in which a thick part 31 on one side and a thin part 32 on the other side are continuous, The upper surface 33 (one surface) is high at the thick portion 31 and is low at the thin portion 32. That is, the upper surface 33 has a substantially sine wave shape that returns from the top dead center 33A that becomes the highest when it goes around the rotation axis 5 to the top dead center 33A through the bottom dead center 33B that becomes the lowest. Further, the cross-sectional shape of the upper surface 33 passing through the rotating shaft 5 is parallel to the lower surface 14A of the protrusion 14 no matter where it is cut, and the space between the upper surface 33 and the lower surface 14A is the compression space 21.

  The top dead center 33A of the swash 9 is movably opposed to the lower surface 14A of the protrusion 14 of the support member 7 through a minute clearance. This clearance is sealed with oil sealed in the sealed container 1. The vane 11 abuts on the upper surface 33 of the swash 9 and divides the compression space 21 in the cylinder 8 into a low pressure chamber LR and a high pressure chamber HR. The coil spring 18 always biases the vane 11 toward the upper surface 33. Further, a minute clearance is formed between the peripheral side surface of the swash 9 and the inner wall of the recessed portion 19 of the cylinder 8, so that the swash 9 is rotatable. The space between the peripheral side surface of the swash 9 and the inner wall of the recessed portion 19 of the cylinder 8 is also sealed with oil.

A discharge valve (not shown) is attached to the outside of the discharge port 28 on the side surface of the recessed portion 19 of the cylinder 8, and a discharge pipe 34 is attached to the upper end of the sealed container 1. An oil sump 36 is formed at the inner bottom of the sealed container 1, and the oil in the oil sump 36 is supplied to the compression element 3 and the like through an oil passage 5 </ b> A provided penetrating through the center of the rotating shaft 5. Will be. Further, a predetermined amount of carbon dioxide (CO ₂ ), R-134a, hydrocarbon-based refrigerant, or the like is enclosed in the sealed container 1.

  With the above configuration, when the stator coil of the stator 4 of the drive element 2 is energized, the rotor 6 rotates in the clockwise direction when viewed from below. The rotation of the rotor 6 is transmitted to the swash 9 through the rotating shaft 5, and thereby the swash 9 rotates in the clockwise direction in the cylinder 8 when viewed from below. Now, the top dead center 33A of the upper surface 33 of the swash 9 is on the vane 11 side of the discharge port 28, and the space surrounded by the cylinder 8, the support member 7, the swash 9 and the vane 11 on the suction port 27 side of the vane 11 (low pressure It is assumed that the refrigerant in the refrigerant circuit is sucked into the compression space 21 from the suction port 27 through the suction pipe 26 and the suction passage 24 into the chamber LR).

  When the swash 9 is rotated from this state, the volume of the space is reduced by the inclination of the upper surface 33 from the stage when the top dead center 33A passes the vane 11 and the suction port 27, and the space (the high pressure chamber HR) is reduced. The refrigerant in) is compressed. The compressed refrigerant is continuously discharged from the discharge port 28 until the top dead center 33A passes through the discharge port 28. On the other hand, after the top dead center 33A passes through the suction port 27, the volume of the space surrounded by the cylinder 8, the support member 7, the swash 9 and the vane 11 on the suction port 27 side of the vane 11 (low pressure chamber LR) increases. Therefore, the refrigerant in the refrigerant circuit is sucked into the compression space 21 from the suction port 27 through the suction pipe 26 and the suction passage 24.

  The refrigerant is discharged from the discharge port 28 into the sealed container 1 through a discharge valve (not shown). The high-pressure refrigerant discharged into the sealed container 1 passes through the air gap between the stator 4 and the rotor 6 of the driving element 2 and is separated from the oil at the upper part in the sealed container 1 (above the driving element 2). The refrigerant is discharged from the discharge pipe 34 to the refrigerant circuit. On the other hand, the separated oil flows down from the gap 10 formed between the sealed container 1 and the stator 4 and returns to the oil reservoir 36.

  With such a configuration, the compressor C can exhibit a sufficient compression function while being small in size and simple in structure. In particular, the lower surface side of the swash 9 is the high pressure in the sealed container 1, and the high pressure and the low pressure are not adjacent to each other in the entire area of the cylinder as in the prior art, and the swash 9 has a continuous thick portion 31 and a thin portion 32. Since one surface is inclined, the seal dimension between the inner wall of the recessed portion 19 of the cylinder 8 can be sufficiently secured in the thick portion 31 corresponding to the high pressure chamber HR.

  As a result, the occurrence of refrigerant leak between the swash 9 and the cylinder 8 can be effectively suppressed, and an effective operation is possible. Further, since the thick portion 31 of the swash 9 serves as a flywheel, torque fluctuation is also reduced. Further, since the compressor C is a so-called internal high-pressure compressor, the structure can be further simplified.

  Since the cylinder 8 has the auxiliary bearing 22 of the rotating shaft 5 located on the side opposite to the supporting member 7, it is not necessary to separately provide a supporting member for the auxiliary shaft of the rotating shaft 5, and the number of parts can be reduced. Further downsizing is possible. Further, since the slot 16 of the vane 11 is formed in the support member 7 and the coil spring 18 is provided in the support member 7, it is not necessary to form a burn mounting structure in the cylinder 8 that requires accuracy, and workability is improved. Is done.

  In the present invention, the suction passage 24 is formed in the support member 7 and a suction port 27 communicating with the suction passage 24 is provided. The refrigerant sucked into the compression space 21 from the suction port 27 is applied to the upper surface 33 of the swash 9. Since the suction port 27 is provided so as to flow in the direction of suction, it is possible to increase the suction cross-sectional area at the time of design, and it is not affected by the side surface 35 of the swash 9 that rotates during the suction process. A reduction in cross-sectional area, an increase in suction resistance, and a decrease in suction amount can be prevented, and performance can be improved.

(Second embodiment of the present invention)
FIG. 6 is a perspective view of a part of a compression element of another compressor of the present invention.
Another compressor C of the present invention is the same as that of the present invention shown in FIGS. 1 to 5 except that a recessed portion 39 is formed on the lower surface portion corresponding to the thick portion 31 of the swash 9 as shown in FIG. This is the same as the compressor C.
The depth of the recessed portion 39 is formed along the inclination of the upper surface 33, and the position corresponding to the top dead center 33A is recessed most deeply.
Since the thick portion 31 and the thin portion 32 are formed in the swash 9, the weight on the thick portion 31 side is larger than the weight on the thin portion 32 side as it is, and weight eccentricity occurs. Therefore, by forming the recessed portion 39, the weight on the thick portion 31 side can be reduced, so that the weight of the swash 9 is made uniform over the entire circumference around the rotation shaft 5, and vibration due to eccentricity can be prevented without using a balance weight. Occurrence can be suppressed.

The description of the above embodiment is for explaining the present invention, and does not limit the invention described in the claims or reduce the scope. Moreover, each part structure of this invention is not restricted to the said embodiment, A various deformation | transformation is possible within the technical scope as described in a claim.
For example, although the description of the above embodiment has been described for the case of a vertical compressor, the compressor of the present invention may be a horizontal compressor. In the case of a horizontal compressor, for example, an oil supply pipe with a pump is connected to the lower end portion of the rotary shaft 5 and one end thereof is inserted into the oil in the oil reservoir 36 to supply the oil. A partition wall that divides the inside of the hermetic container 1 into two is provided between the compression elements 3, and a refrigerant compressed to a high pressure is discharged to the drive element 2 side partitioned by the partition wall to form a high pressure zone, while the partition wall is partitioned by the partition wall. The compression element 3 side is defined as a low pressure area, an oil gap is formed between the outer periphery of the partition wall and the sealed container 1 so as to communicate the high pressure area and the low pressure area, and separated on the drive element 2 side in the sealed container 1. The used oil is circulated and used by flowing out from the gap and returning to the oil reservoir 36.

  Although the compressor of the present invention has a small and simple structure, the high pressure and the low pressure are not adjacent to each other in the entire area of the cylinder as in the conventional case, and the compressor is connected to the cylinder at the thick portion that corresponds to the high pressure chamber. The seal dimension can be secured, the occurrence of refrigerant leakage can be prevented, efficient operation is possible, the thick part of the compression member serves as a flywheel, and torque fluctuations are reduced, and the fluid is compressed by the compression member. Since the suction port is arranged so as to flow toward the upper surface of the suction section, it is possible to increase the suction sectional area at the time of design, and it is not affected by the side surface of the rotating compression member during the suction process. It is possible to prevent the reduction of the suction sectional area, the increase of the suction resistance, and the reduction of the suction amount, and the performance can be improved, so that the industrial utility value is high.

It is a vertical side view explaining an example of the compressor of the present invention. It is another vertical side view of the compressor of this invention shown in FIG. It is a plane longitudinal view of the compressor of this invention shown in FIG. It is a one part perspective view of the compression element of the compressor of this invention shown in FIG. It is a side view of the rotating shaft containing the compression member of the compressor of this invention shown in FIG. It is a one part perspective view of the compression element of the other compressor of this invention. It is a vertical side view of the conventional compressor. FIG. 8 is a plan view of the conventional compressor shown in FIG. 7.

Explanation of symbols

C Compressor LR Low pressure chamber HR High pressure chamber 1 Sealed container 2 Drive element 3 Compression element 4 Stator 5 Rotating shaft 5A Oil passage 6 Rotor 7 Support member 8 Cylinder 9 Compression member (swash)
11 Vane 21 Compression space 24 Suction passage 25 Suction piping 27 Suction port 28 Discharge port 31 Thick part 32 Thin part 33 Upper surface of compression member

Claims (2)

A compression element composed of a cylinder having a compression space therein;
A driving element for driving the compression element; and a rotating shaft for transmitting a rotational force of the driving element to the compression element;
A suction port and a discharge port communicating with the compression space in the cylinder;
One surface is inclined with a continuous thick part and a thin part, and is disposed in the cylinder and rotates, compresses the fluid sucked into the compression space from the suction port, and discharges it from the discharge port. A compression member;
A compressor provided with a vane disposed between the suction port and the discharge port, abutting against one surface of the compression member, and dividing the compression space in the cylinder into a low pressure chamber and a high pressure chamber;
The compressor is characterized in that the suction port is arranged so that the fluid sucked into the compression space from the suction port flows toward the upper surface of the compression member.   The compression element includes a support member that has a main bearing of the rotation shaft and closes the opening of the cylinder, and the cylinder has a sub-bearing of the rotation shaft that is located on the opposite side of the support member. 2. The compressor according to claim 1, wherein a suction passage for sucking fluid in the refrigerant circuit is formed in the support member, and fluid is sucked into the compression space from the suction port via the suction passage. .

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