JP2013072362A - Compressor - Google Patents

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Publication number
JP2013072362A
JP2013072362A JP2011212131A JP2011212131A JP2013072362A JP 2013072362 A JP2013072362 A JP 2013072362A JP 2011212131 A JP2011212131 A JP 2011212131A JP 2011212131 A JP2011212131 A JP 2011212131A JP 2013072362 A JP2013072362 A JP 2013072362A
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Japan
Prior art keywords
eccentric
rotating shaft
oil
bearing
portions
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JP2011212131A
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Japanese (ja)
Inventor
Koki Kamiishida
弘毅 上石田
Naoto Tomioka
直人 富岡
Hiroto Kaida
寛仁 甲斐田
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Daikin Industries Ltd
ダイキン工業株式会社
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Priority to JP2011212131A priority Critical patent/JP2013072362A/en
Publication of JP2013072362A publication Critical patent/JP2013072362A/en
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Abstract

PROBLEM TO BE SOLVED: To suppress, in a compressor with an eccentric rotation type piston mechanism, occurrence of abnormal noise due to vibration in the axial direction of a rotating shaft without increasing sliding loss between a piston and an eccentric portion.SOLUTION: Recessed parts (2a, 2b) for enlarging oil reservoirs (5a, 5b) present between the end faces of headers (31, 35) and the end faces of eccentric parts (1a, 1b) are formed respectively on the end faces of the eccentric parts (1a, 1b).

Description

  The present invention relates to a compressor provided with an eccentric rotary piston mechanism.
  Conventionally, a compressor provided with an eccentric rotation type piston mechanism is known. The eccentric rotary piston mechanism includes a piston that is slidably fitted to an eccentric portion of a rotating shaft that drives the eccentric rotary piston mechanism, and an annular cylinder in which the eccentric portion and a hollow portion that accommodates the piston are formed. And a header portion formed with an end face for closing the hollow opening end of the annular cylinder from the axial direction. In some of these compressors, as shown in Patent Document 1, an oil reservoir is formed between the end surface of the header portion and the end surface of the eccentric portion.
  Specifically, as shown in FIG. 8, the conventional eccentric rotary piston mechanism (50) has a front head (51), a cylinder (52), and a rear head (53) in this order from the upper side to the lower side. These members (51, 52, 53) are stacked and fastened with a plurality of bolts (not shown) extending in the vertical direction. A rotating shaft (54) penetrates these members (51, 52, 53) vertically, and a piston (55) rotatably accommodated in a cylinder (52) is provided on the rotating shaft (54). It is attached. An oil reservoir (56) is formed between the piston (55) and the front head (51) and between the piston (55) and the rear head (53).
  Here, during the drive of the eccentric rotary piston mechanism (50), the rotating shaft (54) may vibrate slightly in the axial direction, and this vibration may cause abnormal noise of the compressor. is there. The oil reservoir (56) has a function of suppressing the noise of the compressor by reducing the vibration of the rotating shaft (54) by using the stored lubricating oil as a buffer material.
Japanese Patent Laid-Open No. 3-70895
  By the way, in the case of the conventional compressor, the outer peripheral edge part of the said eccentric part is notched. Thereby, although the volume of the oil reservoir can be increased, the length of the sliding contact portion between the outer peripheral surface of the eccentric portion and the inner peripheral surface of the piston (hereinafter referred to as the bearing length) is reduced. Decrease. Due to the reduction in the bearing length, there is a problem that the bearing length necessary for forming the oil film is shortened, and the reliability with respect to seizure and wear of the sliding portion between the eccentric portion and the piston is deteriorated.
  Therefore, in order to increase the bearing length, it is necessary to increase the cylinder height. However, if the cylinder height is increased without changing the volume of the cylinder chamber, the outer diameter of the piston is increased and the radial width of the cylinder chamber (distance between the outer peripheral surface of the piston and the inner peripheral surface of the cylinder) Must be reduced. In this case, the cost increases due to an increase in material due to the increase in the size of the piston, and the height gap between the cylinder and the piston increases, which causes deterioration in efficiency due to leakage during refrigerant compression.
  The present invention has been made in view of such a point, and the object thereof is a compressor provided with an eccentric rotation type piston mechanism without deteriorating the reliability of the bearing portion between the piston and the eccentric portion. The object is to suppress the generation of abnormal noise due to the vibration in the axial direction of the rotating shaft.
  A first invention includes a drive mechanism (20) and a compression mechanism (30) driven by a rotation shaft (23) extending from the drive mechanism (20), and the rotation shaft (23) includes the rotation shaft. An eccentric portion (1a, 1b, 1) eccentric from the rotation center of (23) is formed, and the compression mechanism (30) is slidably fitted on the eccentric portion (1a, 1b, 1) ( 40a, 40b), an annular cylinder (32a, 32b) in which a hollow portion for accommodating the eccentric part (1a, 1b, 1) and the piston (40a, 40b) is formed, and the annular cylinder (32a, 32b) is a compressor having a header portion (31, 35) formed with an end face for closing the hollow open end from the axial direction.
  And in this compressor, between the end surface of the said header part (31, 35) and the end surface of the said eccentric part (1a, 1b, 1), the lubricating oil which flows through the inside of the said compression mechanism (30) is shown. On the other hand, an oil reservoir (5a, 5b, 5) is formed. On the end surface of the eccentric part (1a, 1b, 1), a recess (2a, 5b, 5) is formed to enlarge the oil reservoir (5a, 5b, 5). 2b, 2) is formed.
  In the first aspect of the invention, the lubricating oil accumulated in the oil reservoirs (5a, 5b, 5) serves as a cushioning material, so that noise caused by axial vibrations in the rotating shaft (23) is alleviated. Then, by forming recesses (2a, 2b, 2) on the end surfaces of the eccentric parts (1a, 1b, 1), the bearing length between the outer peripheral surface of the eccentric part and the inner peripheral surface of the piston can be reduced. Without changing, the volume of the oil reservoir (5a, 5b, 5) can be increased.
  According to a second aspect, in the first aspect, the compression mechanism (30) includes a slide that slidably supports the rotating shaft (23) through the header portion (31, 35) in the axial direction. A bearing portion (4a, 4b, 4) is formed, and the compression mechanism (6a, 6b) is formed in the bearing gap portion (6a, 6b) between the rotating shaft (23) and the sliding bearing portion (4a, 4b, 4). 30) Lubricating oil circulates, while the recesses (2a, 2b, 2) of the eccentric parts (1a, 1b, 1) are provided at positions that open to the bearing gap parts (6a, 6b). It is characterized by.
  In the second invention, the lubricating oil flowing through the bearing gaps (6a, 6b) of the sliding bearings (4a, 4b, 4) is positively applied to the recesses (2a, 1b, 1) of the eccentric parts (1a, 1b, 1). 2b, 2).
  According to a third invention, in the first or second invention, the compression mechanism (30) penetrates the header portion (31, 35) in the axial direction so that the rotary shaft (23) is slidable. Sliding bearing portions (4a, 4b, 4) to be supported are formed, and the bearing clearances (6a, 6b) between the rotating shaft (23) and the sliding bearing portions (4a, 4b, 4) While the lubricating oil of the compression mechanism (30) flows, the recesses (2a, 2b, 2) of the eccentric part (1a, 1b, 1) are located outside the bearing gap part (6a, 6b) and Communication grooves (8a, 8b) that connect the recesses (2a, 2b, 2) and the bearing gaps (6a, 6b) are formed on the end faces of the eccentric parts (1a, 1b, 1) It is characterized by.
  In the third invention, the recesses (2a, 2b, 2) of the eccentric part (1a, 1b, 1) are located outside the bearing clearance (6a, 6b) in the sliding bearing part (4a, 4b, 4). Is arranged. In this case, the bearing clearance (6a, 6b) is lubricated through the communication groove (8a, 8b) formed between the recess (2a, 2b, 2) and the bearing clearance (6a, 6b). Oil can be actively guided to the recesses (2a, 2b, 2).
  According to a fourth aspect of the present invention, in any one of the first to third aspects, the casing includes a casing (11) that houses the compression mechanism (30) and the drive mechanism (20). An oil flow passage (3) through which lubricating oil stored in the bottom of the casing (11) flows is formed at the center, and the eccentric portion (1a, 1b, 1) is disposed inside the eccentric portion (1a, 1b, 1). , 1b, 1) are formed with communication passages (9a, 9b) that communicate the recesses (2a, 2b, 2) with the oil flow passage (3).
  In 4th invention, the communicating path (9a, 9b) which connects the recessed part (2a, 2b, 2) of the said eccentric part (1a, 1b, 1) and the oil flow path (3) of the said rotating shaft (23) Thus, the lubricating oil in the oil flow passage (3) can be guided directly to the recesses (2a, 2b, 2). The lubricating oil in the oil flow passage (3) is different from the lubricating oil in the bearing clearance (6a, 6b), and the sliding part between the rotating shaft (23) and the sliding bearing (4a, 4b, 4). Is not flowing. For this reason, the temperature of the lubricating oil in the oil flow passage (3) is lower than the temperature of the lubricating oil in the bearing gap (6a, 6b). As a result, a relatively high-viscosity lubricating oil can be guided to the recesses (2a, 2b, 2).
  According to a fifth invention, in any one of the first to fourth inventions, a recess (50a, 5b, 5) for enlarging the oil reservoir (5a, 5b, 5) is formed on the end surface of the header (31, 35). 50b) is formed.
  In the fifth aspect of the present invention, the recesses (50a, 50b) are formed on the end surfaces of the header portions (31, 35), so that the volume of the oil sump portions (5a, 5b, 5) can be further expanded. become.
  According to the present invention, the concave portion (2a, 2b, 2) is formed on the end surface of the eccentric portion (1a, 1b, 1), so that the outer peripheral surface of the eccentric portion (1a, 1b, 1) and the piston ( The volume of the oil reservoir (5a, 5b, 5) can be increased without changing the bearing length between the inner peripheral surfaces of 40a, 40b). Thereby, generation | occurrence | production of the abnormal noise by the vibration of the said rotating shaft (23) can be relieved. Further, since the bearing length does not change, the gap in the height direction between the cylinders (32a, 32b) and the pistons (40a, 40b) does not change, so that the efficiency is not deteriorated due to leakage during refrigerant compression.
  According to the second aspect of the present invention, the lubricating oil flowing through the bearing clearances (6a, 6b) of the sliding bearings (4a, 4b, 4) is positively applied to the eccentric parts (1a, 1b, 1). To the recesses (2a, 2b, 2) of the oil reservoir, and the lack of lubricating oil in the oil reservoirs (5a, 5b, 5) is suppressed. Thereby, generation | occurrence | production of the noise by the vibration of the said rotating shaft (23) can be relieve | moderated reliably.
  Further, according to the third aspect of the present invention, even when the concave portion (2a, 2b, 2) of the eccentric portion (1a, 1b, 1) is located outside the bearing gap portion (6a, 6b), Through the communication groove (8a, 8b), the lubricating oil in the bearing gap (6a, 6b) can be actively guided to the recess (2a, 2b, 2). Thereby, the shortage of lubricating oil in the oil reservoirs (5a, 5b, 5) is suppressed, and the generation of noise due to the vibration of the rotating shaft (23) can be further alleviated.
  According to the fourth aspect of the invention, the lubricating oil in the oil flow passage (3) can be directly guided to the recesses (2a, 2b, 2) through the communication passages (9a, 9b). As described above, since the lubricating oil in the oil flow passage (3) has a higher viscosity than the lubricating oil in the bearing gap (6a, 6b), the effect of the lubricating oil as a buffer material is enhanced. Thereby, generation | occurrence | production of the abnormal noise by the vibration of the said rotating shaft (23) can be relieved.
  According to the fifth aspect of the invention, the recesses (50a, 50b) are formed in the end faces of the header portions (31, 35), thereby further expanding the volume of the oil sump portions (5a, 5b, 5). Can be made. As a result, the amount of lubricating oil in the oil reservoirs (5a, 5b, 5) increases, and the effect of this lubricating oil as a buffer material can be enhanced.
FIG. 1 is a longitudinal sectional view of a compressor according to this embodiment. FIG. 2 is a cross-sectional view of a cylinder portion of the compressor according to the present embodiment. FIG. 3 is a schematic view of the vicinity of the oil reservoir according to the present embodiment. FIG. 4 is a schematic view of the vicinity of an oil reservoir according to the compressor of the first modification. FIG. 5 is a schematic view of the vicinity of an oil reservoir according to the compressor of the second modification. FIG. 6 is a longitudinal sectional view of the compressor of the third modification. FIG. 7 is a longitudinal sectional view of a compressor according to another embodiment. FIG. 8 is a longitudinal sectional view of an eccentric rotary piston mechanism of a conventional compressor.
  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. First, after describing the compressor (10) according to the embodiment of the present invention, a buffer unit that alleviates abnormal noise caused by vertical vibration of the rotating shaft (23) in the compressor (10) will be described.
<Overall structure of compressor>
FIG. 1 is a longitudinal sectional view of a compressor (10) according to the present embodiment. The compressor (10) is connected to a refrigerant circuit that performs a vapor compression refrigeration cycle, and includes a casing (11), an electric motor (20), an eccentric rotary piston mechanism (compression mechanism) (30), It has.
<casing>
The casing (11) is composed of a vertically long cylindrical sealed container with both ends closed, and a cylindrical body (12) and an upper end plate (13) closing the upper end side of the body (12) A lower end plate (14) for closing the lower end side of the body (12). First and second inlet tubes (15a, 15b) are attached to the body part (12) through the lower part of the body part (12). A discharge pipe (16) is attached through the upper part of the upper end plate (13). The electric motor (20) and the eccentric rotary piston mechanism (30) are accommodated in the casing (11). An oil sump (17) is formed at the bottom of the lower end plate (14). The oil reservoir (17) stores lubricating oil that lubricates the sliding portion of the compression mechanism (30).
<Electric motor>
The electric motor (20) includes a stator (21) and a rotor (22) both formed in a cylindrical shape. The stator (21) is fixed to the body (12) of the casing (11). The rotor (22) is disposed in the hollow portion of the stator (21). A rotating shaft (23) is fixed in the hollow portion of the rotor (22) so as to penetrate the rotor (22), and the rotor (22) and the rotating shaft (23) rotate integrally. ing.
<Axis of rotation>
The rotating shaft (23) has a main shaft portion (24) extending vertically. An upper eccentric portion (1a) and a lower eccentric portion (1b) are integrally formed near the lower end of the main shaft portion (24). The upper eccentric part (1a) is located above the lower eccentric part (1b). These eccentric portions (1a, 1b) are each formed to have a larger diameter than the main shaft portion (24). The axis of the upper eccentric part (1a) and the lower eccentric part (1b) is eccentric by a predetermined distance with respect to the axis of the main shaft part (24), and the upper eccentric part (1a) and the lower eccentric part (1b ) Are deviated from each other by 180 degrees. Further, the outer peripheral edges of both end faces of these eccentric portions (1a, 1b) are tapered over the entire circumference.
  On the upper end surface of the upper eccentric portion (1a) and the lower end surface of the lower eccentric portion (1b), arc-shaped concave portions (2a, 2b) are formed, respectively, as viewed in a cross section perpendicular to the axis.
  An oil supply passage (oil communication passage) (3) is formed inside the rotary shaft (23). The inflow end of the oil supply passage (3) communicates with a centrifugal pump (25) formed at the lower end of the rotating shaft (23). The oil supply passage (3) has a plurality of outflow ends. These outflow ends constitute an oil supply hole that opens on the outer peripheral surface of the rotating shaft (23). In the present embodiment, first to fifth oil supply holes (7a, 7b, 7c, 7d, 7e) are formed from the upper side to the lower side.
  The centrifugal pump (25) is operated along with the rotation of the rotary shaft (23), and the lubricating oil in the oil reservoir (17) in the casing (11) is pumped up to the oil supply passage (3). It flows out from the first to fifth oil supply holes (7a, 7b, 7c, 7d, 7e). This lubricating oil flows to the sliding portion of the eccentric rotary piston mechanism (30) and is also used for lubricating the sliding portion.
<Eccentric rotating piston mechanism>
As shown in FIG. 1, the eccentric rotary piston mechanism (30) includes a front head (31), an upper cylinder (32a), a middle plate (33), a lower cylinder (32b) from the upper side to the lower side. ) And the rear head (35) in this order, and these members (31, 32a, 33, 32b, 35) are fastened by a plurality of bolts extending in the vertical direction. And the said rotating shaft (23) has penetrated these members (31, 32a, 33, 32b, 35) up and down.
-Front head-
A through-hole portion that penetrates the front head (31) in the thickness direction is formed in the center portion of the front head (31). The inner peripheral surface of the through-hole portion constitutes an upper bearing portion (sliding bearing portion) (4a) that rotatably supports the main shaft portion (24) of the rotating shaft (23). An upper bearing gap (6a) is formed between the inner peripheral surface of the upper bearing portion (4a) and the outer peripheral surface of the main shaft portion (24). Lubricating oil is supplied to the upper bearing clearance (6a) through the oil supply passage (3) of the rotating shaft (23).
  Here, the lower end opening edge of the front head (31) is cut out over the entire circumference. The lower end of the upper bearing gap (6a) is enlarged by this notch. This enlarged portion is the enlarged portion (18a) of the upper bearing gap portion (6a).
  Further, an upper discharge port (46) penetrating in the thickness direction is formed outside the center portion of the front head (31) (see FIG. 2). The upper discharge port (46) intermittently communicates with a compression chamber (45a) formed in the upper cylinder (32a).
  A first muffler cover (37a) covering the upper discharge port (46) and a second muffler cover (37b) covering the first muffler cover (37a) are provided on the upper surface of the front head (31). Is provided. The first muffler cover (37a) has a communication hole (not shown) that communicates the first muffler space (38a) of the first muffler cover (37a) and the second muffler space (38b) of the second muffler cover (37b). None) is provided. The second muffler cover (37b) is provided with a communication hole (not shown) that communicates the second muffler space (38b) and the internal space of the casing (11).
  The second muffler space (38b) has a refrigerant passage (not shown) extending in the axial direction from the lower discharge chamber (26) formed in the rear head (35). The refrigerant passage is formed so as to penetrate the eccentric rotary piston mechanism (30).
-Rear head-
A through-hole portion that penetrates the rear head (35) in the thickness direction is formed in the central portion of the rear head (35). The inner peripheral surface of the through hole portion constitutes a lower bearing portion (4b) that rotatably supports the main shaft portion (24) of the rotating shaft (23). A lower bearing gap (6b) is formed between the inner peripheral surface of the lower bearing portion (sliding bearing portion) (4b) and the outer peripheral surface of the main shaft portion (24). Lubricating oil is supplied to the lower bearing gap (6b) through the oil supply passage (3) of the rotating shaft (23).
  Here, the outer edge of the upper end surface opening of the rear head (35) is cut out over the entire circumference. Due to this notch, the lower end of the lower bearing gap (6b) is enlarged. This enlarged portion is the enlarged portion (18b) of the lower bearing gap (6b).
  A lower discharge chamber (26) is formed inside the rear head (35) outside the lower bearing portion (4b). The rear head (35) is formed with a lower discharge port (not shown) that extends from the lower discharge chamber (26) and opens at the upper end surface of the rear head (35). The lower discharge chamber (26) and a compression chamber (not shown) formed inside the lower cylinder (32b) communicate with each other through the lower discharge port.
-Middle plate-
A through-hole portion that penetrates the front head (31) in the thickness direction is formed in the center portion of the middle plate (33). The main shaft portion (24) of the rotating shaft (23) is located inside the through portion.
-Upper cylinder and lower cylinder-
Since the upper cylinder and the lower cylinder (32a, 32b) have substantially the same configuration, the upper cylinder (32a) will be described, and the description of the lower cylinder (32b) will be partially omitted.
  A substantially circular through-hole portion that penetrates the upper cylinder (32a) in the thickness direction is formed in the central portion of the upper cylinder (32a). The upper end opening surface of the upper cylinder (32a) is closed by the lower end surface of the front head (31), and the lower end opening surface of the upper cylinder (32a) is closed by the upper end surface of the middle plate (33). The through hole portion of (32a) becomes the upper cylinder chamber (39a). The upper cylinder chamber (39a) accommodates an upper piston (40a) that is slidably fitted to the upper eccentric portion (1a) of the rotating shaft (23).
  In the case of the lower cylinder (32b), the upper end opening surface of the lower cylinder (32b) is closed by the lower end surface of the middle plate (33), and the lower end opening surface of the lower cylinder (32b) is the rear head ( It is blocked at the upper end surface of 35). The cylinder chamber (39b) of the lower cylinder (32b) accommodates a lower piston (40b) that is slidably fitted to the lower eccentric portion (1b) of the rotating shaft (23). .
  As shown in FIG. 2, the upper cylinder (32a) is formed with a bush groove (42) that partially opens into the upper cylinder chamber (39a) in plan view. The bush groove (42) is a circular groove, and a blade (41) of an upper piston (40a) described later is located in the bush groove (42).
  In the bush groove (42), a pair of bushes (43) formed in a half-moon shape in plan view is fitted in a state of sandwiching the low-stage blade (41). The arc surface of the bush (43) can be slidably contacted with the inner peripheral surface of the bush groove (42), and the flat surface of the bush (43) is in contact with the side surface of the blade (41). Sliding contact is possible.
  The upper cylinder (32a) is formed with a suction through passage (44) that penetrates radially between the inner peripheral surface and the outer peripheral surface of the upper cylinder (32a). The end of the first inlet tube (15a) is inserted and fixed in the suction through passage (44).
  In the case of the lower cylinder (32b), the end of the second inlet tube (15b) is inserted and fixed in the suction passage of the lower cylinder (32b).
-Upper piston and lower piston-
Since the upper piston (40a) and the lower piston (40b) have the same configuration, the upper piston (40a) will be described, and the description of the lower piston (40b) will be omitted.
  As shown in FIG. 2, the upper piston (40a) has a through-hole portion that penetrates in the thickness direction of the upper piston (40a). The upper eccentric part (1a) of the rotating shaft (23) is slidably fitted in the through hole.
  The upper piston (40a) includes a blade (41) projecting radially outward from the outer peripheral surface of the upper piston (40a). As described above, the blade (41) is sandwiched between the pair of blades (43) so as to freely advance and retract. The outer peripheral surface of the upper piston (40a) is formed as a cylindrical surface except for the peripheral edge of the blade (43).
  The blade (41) divides the upper cylinder chamber (39a) into a compression chamber (45a) and a suction chamber (45b). As described above, the upper discharge port (46) of the front head (31) communicates with the compression chamber (45a) intermittently. On the other hand, the suction through passage (44) communicates with the suction chamber (45b) intermittently.
  The movement of the upper piston (40a) is such that a part of the cylindrical surface of the upper piston (40a) and a part of the inner peripheral surface (35) of the cylinder (32) are always substantially in pressure contact ( Strictly speaking, there is a minute gap on the order of microns, but leakage of the refrigerant in the minute gap is not a problem.
<Compressor buffer>
As shown in FIG. 1, the eccentric rotary piston mechanism (30) includes an upper oil reservoir (5a) between a lower end surface of the front head (31) and an upper end surface of the upper eccentric portion (1a). ) Is formed. Further, a lower oil reservoir (5b) is formed between the upper end surface of the rear head (35) and the lower end surface of the lower eccentric portion (1b). Each of the oil reservoirs (5a, 5b) constitutes a buffer part of the compressor (10). Due to the lubricating oil accumulated in the oil reservoirs (5a, 5b), abnormal noise due to the vertical vibration of the rotating shaft (23) is reduced.
  Here, as described above, concave portions (2a, 2b) are formed in the eccentric portions (1a, 1b). Each recess (2a, 2b) is open to each oil reservoir (5a). Thereby, the volume of each oil sump part (5a) is expanding.
  A line A in FIG. 3 shows the outline of the outer peripheral edge of the main shaft portion (24) of the rotating shaft (23). Moreover, the B line | wire of FIG. 3 has shown the outline of the outer periphery of the expansion part (18a, 18b) in each bearing clearance gap part (6a, 6b).
  As shown in FIG. 3, each recessed part (2a, 2b) is provided in the position opened in a part of enlarged part (18a, 18b) of each said bearing clearance gap part (6a, 6b). As a result, the lubricating oil flowing through the bearing gaps (6a, 6b) can easily flow into the recesses (2a, 2b).
-Driving action-
In the compressor (10), when the rotating shaft (23) of the electric motor (20) rotates, the pistons (40a, 40b) attached to the eccentric portions (1a, 1b) of the rotating shaft (23) are cylinders. It rotates eccentrically in the chamber (39a, 39b). As a result, the volumes of the compression chambers and suction chambers of the pistons (40a, 40b) and cylinder chambers (39a, 39b) fluctuate periodically. Is performed continuously.
  The refrigerant sucked from the inlet tubes (15a, 15b) into the suction chambers of the cylinder chambers (39a, 39b) is compressed in the compression chambers of the cylinder chambers (39a, 39b) and then discharged from the discharge ports. Discharged. The refrigerant discharged from the upper discharge port (46) flows into the first muffler space (38a). On the other hand, the refrigerant discharged from the lower discharge port (46) passes through the refrigerant through path of the lower discharge chamber (26) and the eccentric rotary piston mechanism (30), and then the second muffler space ( 38b).
  The refrigerant in the first muffler space (38a) merges with the refrigerant in the second muffler space (38b) through the communication hole of the first muffler cover (37a), and then passes through the communication hole of the second muffler cover (37b). It flows into the internal space of the casing (11). The refrigerant flows out of the casing (11) through the discharge pipe (16) of the casing (11).
  In the rotating shaft (23), as described above, the lubricating oil pumped up by the centrifugal pump (25) flows out from the oil supply holes (7a, 7b, 7c, 7d, 7e). Here, the lubricating oil flowing out from the second oil supply hole (7b) passes through the enlarged portion (18a) of the upper bearing clearance (6a) in the upper bearing portion (4a), and then the upper oil reservoir (5a). And the concave portion (2a) of the upper eccentric portion (1a).
  The lubricating oil flowing out from the fifth oil supply hole (7e) passes through the enlarged portion (18b) of the lower bearing clearance (6b) in the lower bearing portion (4b), and then the lower oil reservoir (5b). And the recess (2b) of the lower eccentric part (1b). In this way, the lubricating oil is supplied to each oil reservoir (5a, 5b).
-Effect of the embodiment-
According to this embodiment, the bearing length between the outer peripheral surface of the eccentric part and the inner peripheral surface of the piston is formed by forming the recesses (2a, 2b) in the end faces of the eccentric part (1a, 1b). The volume of the oil reservoir (5a, 5b) can be increased without changing the above. Thereby, generation | occurrence | production of the abnormal noise by the vibration of the said rotating shaft (23) can be relieved. Further, since the bearing length described above does not change, the gap in the height direction between the cylinder and the piston does not change, so that the efficiency is not deteriorated due to leakage during refrigerant compression.
  Further, according to this embodiment, the lubricating oil flowing through the bearing gaps (6a, 6b) of the bearings (4a, 4b) is positively applied to the recesses (2a, 2b) of the eccentric parts (1a, 1b). The shortage of lubricating oil in the oil reservoirs (5a, 5b) is suppressed. Thereby, generation | occurrence | production of the noise by the vibration of the said rotating shaft (23) can be relieved reliably.
-Modification 1 of embodiment-
In the first modification of the above-described embodiment shown in FIG. 4, unlike the above-described embodiment, communication grooves (8a, 8b) are formed on the end surfaces of the eccentric portions (1a, 1b). The communication grooves (8a, 8b) communicate the recesses (2a, 2b) of the eccentric portions (1a, 1b) with the enlarged portions (18a, 18b) of the bearing gap portions (6a, 6b). As a result, even when the recesses (2a, 2b) are arranged outside the bearing gaps (6a, 6b), the bearing gaps (6a, 6b) are lubricated through the communication grooves (8a, 8b). Oil can be actively guided to the recesses (2a, 2b).
  Thereby, the shortage of lubricating oil in the oil reservoirs (5a, 5b) is suppressed, and the generation of noise due to the vibration of the rotating shaft (23) can be further alleviated.
-Modification 2 of embodiment-
In the second modification of the above embodiment shown in FIG. 5, unlike the above embodiment, communication paths (9a, 9b) are formed inside the eccentric portions (1a, 1b). The communication passages (9a, 9b) communicate the recesses (2a, 2b) of the eccentric portions (1a, 1b) with the oil supply passage (3) of the rotating shaft (23). As a result, even when the recesses (2a, 2b) are arranged outside the bearing gaps (6a, 6b), the lubricating oil in the oil supply passage (3) is directly passed through the communication passages (9a, 9b). Thus, it can be guided to the recesses (2a, 2b).
  Here, the lubricating oil in the oil supply passage (3) is different from the lubricating oil in the bearing gap (6a, 6b), and the sliding between the piston (40a, 40b) and the sliding bearing (4a, 4b). Not flowing part. For this reason, the temperature of the lubricating oil in the oil flow passage (3) is lower than the temperature of the lubricating oil in the bearing gap (6a, 6b). Thereby, the effect as a buffer material of lubricating oil can be heightened by guide | inducing lubricating oil with comparatively high viscosity to the said recessed part (2a, 2b). As a result, the generation of abnormal noise due to the vibration of the rotating shaft (23) can be reliably mitigated.
—Modification 3 of Embodiment—
6 differs from the above embodiment in that the oil sump portions (5a, 5b) are provided on the lower end surface of the front head (31) and the upper end surface of the rear head (35). An expanding recess (50a, 50b) is formed. As a result, the volume of the oil reservoir (5a, 5b) can be further increased, the amount of lubricating oil in the oil reservoir (5a, 5b) is increased, and the effect of this lubricating oil as a buffer material is enhanced. be able to.
<< Other Embodiments >>
About the said embodiment, it is good also as the following structures.
  In the present embodiment, the eccentric rotary piston mechanism (30) has two cylinders (32a, 32b) on the upper and lower sides. However, the present invention is not limited to this, and as shown in FIG. There may be only one (32). Even in this case, the volume of the oil reservoir (5) can be increased by forming the recesses (2) on both end faces of the eccentric part (1).
  Moreover, in this embodiment, although the recessed part (2a, 2b) was formed in both eccentric parts (1a, 1b), it is not necessary to be limited to this, and one side of both eccentric parts (1a, 1b) Only the recesses (2a, 2b) may be formed.
  In addition, the above embodiment is an essentially preferable illustration, Comprising: It does not intend restrict | limiting the range of this invention, its application thing, or its use.
  As described above, the present invention is useful for a compressor provided with an eccentric rotation type piston mechanism.
1a, 1b Eccentric part
2a, 2b recess
3 Oil supply passage (oil communication passage)
4a, 4b Bearing part (sliding bearing part)
5a, 5b Oil reservoir
6a, 6b Bearing clearance
10 Compressor
20 Electric motor (drive mechanism)
23 Rotation axis
30 Eccentric rotating piston mechanism (compression mechanism)
31 Front head
35 Rear head
32a, 32b cylinder
40a, 40b piston

Claims (5)

  1. A drive mechanism (20) and a compression mechanism (30) driven by a rotating shaft (23) extending from the drive mechanism (20);
    The rotating shaft (23) is formed with an eccentric portion (1a, 1b, 1) eccentric from the rotation center of the rotating shaft (23),
    The compression mechanism (30) includes a piston (40a, 40b) slidably fitted to the eccentric portion (1a, 1b, 1), the eccentric portion (1a, 1b, 1), and the piston (40a, 40b) is formed with an annular cylinder (32a, 32b) in which a hollow part is formed, and a header part (31, 32b) in which an end face for closing the hollow open end of the annular cylinder (32a, 32b) from the axial direction is formed. 35) having a compressor,
    An oil reservoir (5a, 5b) in which lubricating oil flowing inside the compression mechanism (30) accumulates between the end face of the header part (31, 35) and the end face of the eccentric part (1a, 1b, 1) , 5) is formed,
    A compressor characterized in that recesses (2a, 2b, 2) for enlarging the oil sump portions (5a, 5b, 5) are formed on end surfaces of the eccentric portions (1a, 1b, 1).
  2. In claim 1,
    The compression mechanism (30) is formed with sliding bearing portions (4a, 4b, 4) that pass through the header portions (31, 35) in the axial direction and slidably support the rotating shaft (23). ,
    In the bearing clearance (6a, 6b) between the rotating shaft (23) and the sliding bearing (4a, 4b, 4), the lubricating oil of the compression mechanism (30) flows.
    The compressor characterized in that the recesses (2a, 2b, 2) of the eccentric part (1a, 1b, 1) are provided at positions that open to the bearing gap parts (6a, 6b).
  3. In claim 1 or 2,
    The compression mechanism (30) is formed with sliding bearing portions (4a, 4b, 4) that pass through the header portions (31, 35) in the axial direction and slidably support the rotating shaft (23). ,
    In the bearing clearance (6a, 6b) between the rotating shaft (23) and the sliding bearing (4a, 4b, 4), the lubricating oil of the compression mechanism (30) flows.
    The recesses (2a, 2b, 2) of the eccentric part (1a, 1b, 1) are located outside the bearing gap part (6a, 6b),
    Communication grooves (8a, 8b) are formed on the end surfaces of the eccentric portions (1a, 1b, 1) to communicate the recesses (2a, 2b, 2) with the bearing gap portions (6a, 6b). A compressor characterized by that.
  4. In any one of Claims 1-3,
    A casing (11) for accommodating the compression mechanism (30) and the drive mechanism (20);
    An oil flow passage (3) through which lubricating oil stored at the bottom of the casing (11) flows is formed at the center of the rotating shaft (23),
    The eccentric portion (1a, 1b, 1) has a communication passage (9a) that connects the concave portion (2a, 2b, 2) of the eccentric portion (1a, 1b, 1) and the oil flow passage (3). , 9b).
  5. In any one of Claims 1-4,
    A compressor characterized in that recesses (50a, 50b) for enlarging the oil sump portions (5a, 5b, 5) are formed on end faces of the header portions (31, 35).
JP2011212131A 2011-09-28 2011-09-28 Compressor Withdrawn JP2013072362A (en)

Priority Applications (1)

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JP2011212131A JP2013072362A (en) 2011-09-28 2011-09-28 Compressor

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104612970A (en) * 2015-01-23 2015-05-13 珠海凌达压缩机有限公司 Pump body structure and compressor
CN105134603A (en) * 2015-08-05 2015-12-09 广东美芝制冷设备有限公司 Compressor
WO2020121443A1 (en) * 2018-12-12 2020-06-18 東芝キヤリア株式会社 Rotary compressor and refrigeration cycle device

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104612970A (en) * 2015-01-23 2015-05-13 珠海凌达压缩机有限公司 Pump body structure and compressor
CN105134603A (en) * 2015-08-05 2015-12-09 广东美芝制冷设备有限公司 Compressor
WO2020121443A1 (en) * 2018-12-12 2020-06-18 東芝キヤリア株式会社 Rotary compressor and refrigeration cycle device

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