JP2006132346A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a highly reliable compressor which achieves long service life by preventing slide wear between a vane and a rotary shaft so that one side surface of the vane does not slide in a state of direct abutment onto the outer peripheral surface of the rotary shaft. <P>SOLUTION: A compressor C is equipped with a compressing element 3 composed of a cylinder 8 which forms a compressing space 21 thereinside, a drive element 2, a rotary shaft 5, a suction and discharge ports, a compressing member 9 which includes a thick part 31 and a thin part 32 continued with one surface thereof inclined and which is disposed in the cylinder 8 to be rotated so as to compress the fluid sucked through the suction port and to discharge the fluid through the discharge port, and a vane disposed between the suction port and discharge port and abutted to one surface 33 of the compressing member 9 so as to partition the compressing space 21 in the cylinder 8 into a low pressure chamber LR and a high pressure chamber HR. A roller ring 40 is inserted and arranged in the outer periphery of the rotation shaft 5 corresponding to the vane so as to abut one side surface of the vane onto the outer periphery of the roller ring 40. <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

  However, in the compressor previously proposed by the present inventors, one side surface of the vane that divides the compression space in the cylinder into a low pressure chamber and a high pressure chamber slides in direct contact with the outer peripheral surface of the rotating shaft. Since it was configured, there was a problem that sliding wear between the vane and the rotating shaft was large, and the life was shortened.

  The object of the present invention is to prevent one side surface of the vane from directly abutting on the outer peripheral surface of the rotating shaft to slide, thereby preventing sliding wear between the vane and the rotating shaft, extending the service life, and ensuring reliability. To provide a high compressor.

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;
A compression member that has a continuous thick part and a thin part and has one inclined surface, is disposed in the cylinder and rotates, compresses the fluid sucked from the suction port, and discharges it from the discharge port;
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;
A roller ring is inserted and arranged on the outer periphery of the rotating shaft corresponding to the vane so as to be rotatable, and one side surface of the vane is in contact with the outer peripheral surface of the roller ring. .

  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, and the cylinder. Has a sub-bearing of the rotating shaft located on the opposite side of the support member, and both end portions of the roller ring are in contact with receiving portions formed by recessing the corresponding support member and the compression member. It is characterized by having made it.

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 from the suction port and discharges the fluid from the discharge port; and is disposed between the suction port and the discharge port and abuts against one surface of the compression member, so that the compression space in the cylinder A compressor including a vane that divides the gas into a low pressure chamber and a high pressure chamber,
A roller ring is inserted and arranged on the outer periphery of the rotating shaft corresponding to the vane so as to be able to rotate, and one side surface of the vane is in contact with the outer peripheral surface of the roller ring. ,
Although it is a small and simple structure, high pressure and low pressure are not adjacent to each other in the entire area of the cylinder as in the conventional case, and the seal dimension between the cylinder and the thick part that corresponds to the high pressure chamber can be secured. In addition, the occurrence of refrigerant leakage can be prevented, efficient operation becomes possible, and the thick wall portion of the compression member plays the role of a flywheel, so torque fluctuations are reduced.
Since one side surface of the vane slides in contact with the outer peripheral surface of the roller ring, sliding resistance is eased, sliding wear between the vane and the rotating shaft can be prevented, and a longer life can be achieved. There is a remarkable effect that the reliability is 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 both end portions of the roller ring are contacted with receiving portions formed by recessing the corresponding support member and the compression member. This eliminates the need for a separate support member for the secondary bearing of the rotating shaft, reduces the number of parts and further reduces the size of the roller ring, and ensures that the roller ring is in place. Therefore, it is possible to reliably prevent sliding wear between the vane and the rotating shaft, and to further improve the reliability.

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)
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, FIG. 3 is a plan sectional view of the compressor C, and FIG. 5 is a perspective view of a part of the compression element 3 of the compressor C. FIG. 5 is a side view of the roller ring 40 including the compression member 9 and the rotary shaft 5. FIG. 6A is a perspective view of the key 11 and the roller ring 40. 6B shows longitudinal side views of the key 11 and the roller ring 40, respectively.

  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.

  A slot 16 is formed in the protruding portion 14 of the support member 7, and the vane 11 is inserted into the slot 16 so as to be capable of reciprocating 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. A suction passage 24 is formed in the cylinder 8, and a suction pipe 26 is attached to the sealed container 1 and connected to the suction passage 24. The cylinder 8 is formed with a suction port 27 and a discharge port 28 that communicate with the compression space 21, the suction passage 24 communicates with the suction port 27, and the discharge port 28 communicates with the inside of the sealed container 1 at the side surface of the cylinder 8. is doing. The vane 11 is located between the suction port 27 and the discharge port 28.

A roller ring 40 is inserted into the outer periphery of the rotary shaft 5 corresponding to the vane 11 so as to be able to rotate, and one side surface of the vane 11 abuts on the outer peripheral surface of the roller ring 40 and slides. The upper and lower ends of the roller ring 40 are slid in contact with the receiving portions 7A and 9A formed in the corresponding support members 7 and swashes 9, respectively.
Oil sealed in the sealed container 1 is between the rotating shaft 5 and the roller ring 40, between one side surface of the vane 11 and the roller ring 40, and between the upper and lower ends of the roller ring 40 and the receiving portions 7A and 9A. Is sealed by.
The rotary shaft 5 is inserted through the central portion of the support member 7 and the cylinder 8 and is pivotally supported by the main bearing 13 at the central portion in the vertical direction. The lower end is pivotally 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 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 roller ring 40 is inserted into the outer periphery of the rotary shaft 5 corresponding to the vane 11 so as to be able to rotate, and one side surface of the vane 11 abuts on the outer peripheral surface of the roller ring 40 and slides. As a result, the sliding resistance is alleviated, the sliding wear of the vane 11 and the rotating shaft 5 can be prevented, the life can be extended, and the reliability can be improved. Further, since the upper and lower ends of the roller ring 40 are brought into contact with the receiving portions 7A and 9A formed by recessing the corresponding support member 7 and compression member 9, the roller ring 40 can be reliably disposed at a predetermined position. The sliding resistance is reliably relieved, the sliding wear between the vane 11 and the rotary shaft 5 can be surely prevented, and the reliability is further improved.

(Second embodiment of the present invention)
FIG. 7 shows a perspective view of the compression member 9 of another compressor C of the present invention as viewed from below.
Another compressor C of the present invention is the same as that of the present invention shown in FIGS. 1 to 6 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 becomes possible, the thick part of the compression member acts as a flywheel, and torque fluctuation is reduced, and one side of the vane Since it slides in contact with the outer peripheral surface of the roller ring, the sliding resistance is relaxed, sliding wear between the vane and the rotating shaft can be prevented, the life can be extended, and the reliability is improved. Since it has a remarkable effect, it has high industrial utility value.

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 sectional view of the compressor of the present 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 which inserted and arrange | positioned the roller ring containing the compression member of the compressor of this invention shown in FIG. (A) is a perspective view of the vane and roller ring of the compressor of the present invention shown in FIG. 1, and (B) is a longitudinal side view of the vane and roller ring of the compressor of the present invention shown in FIG. It is a perspective view explaining the other compression member of the compressor of this invention.

Explanation of symbols

C Compressor LR of the present invention 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 7A Receiving portion 8 Cylinder 9 Compression member (swash)
9A Receiving part 11 Vane 21 Compression space 27 Suction port 28 Discharge port 31 Thick part 32 Thin part 33 Upper surface 40 of compression member Roller ring

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;
A compression member that has a continuous thick part and a thin part and has one inclined surface, is disposed in the cylinder and rotates, compresses the fluid sucked from the suction port, and discharges it from the discharge port;
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;
A compressor characterized in that a roller ring is inserted and arranged on the outer periphery of the rotating shaft corresponding to the vane so as to be able to rotate, and one side surface of the vane abuts on the outer peripheral surface of the roller ring.   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 both end portions of the roller ring are brought into contact with corresponding support members and receiving portions formed by recessing the compression members.

Images