CN1034968C - Horizontal rotary compressor - Google Patents

Abstract

An object of the present invention is to improve the lubricating performance of lubricating oil supplied to bearings of a horizontal rotary compressor. Comprising the electric motor and the compression part 12 connected by the crankshaft 15 in the sealed casing, the first cylinder 16 and the second cylinder 17 constituting the above-mentioned compression part 12 are arranged continuously between the two sides of the partition plate 18, and the sliding surface of the compression part 12 is forced to An oil feed pump for supplying lubricating oil is provided on the outer peripheral surface of the crank 22 and 23 of the crankshaft 15 to guide the lubricating oil supplied by the oil pump to the bearings 20 and 21. Oil grooves 38, 39 are used to limit the flow of lubricating oil to Sealing portions 41, 42 on the side of the plate 18.

Description

Horizontal rotary compressor

The present invention relates to a horizontal rotary compressor used in refrigeration cycle, especially related to the horizontal rotary compressor which improves the structure of the oil groove so that the lubricating oil for lubricating the main bearing and the auxiliary bearing can be fully distributed.

Japanese Patent Laid-Open Publication No. 63-162991 and Utility Model Laid-Open Publication No. 63-118390 disclose a compressor whose two cylinders are connected by a partition. The horizontal rotary compressor shown in FIG. 7 has a structure similar to that of the vertical rotary compressor shown in the above-mentioned Unexamined Patent Publication No. 63-118390, and reference numeral 60 denotes the overall structure of the compression part. The crankshaft 61 connected with the electric motor not shown in the figure is rotatably supported on the main bearing 64 and the auxiliary bearing 65, between the main bearing 64 and the auxiliary bearing 65, it is arranged in an overlapping manner and is separated by a plate separator 59 Separate the two cylinders of the first cylinder 62 and the second cylinder 63 .

The crankshaft 61 is integrally provided with eccentric cranks 66 and 67, and for the first cylinder 62, the cylinder chamber is formed by a roller piston (ロ-ラ) 68 and a sliding plate 80 embedded on the crank 66, and likewise , the cylinder chamber of the second cylinder 63 is formed by the roller piston 69 and the sliding plate 79 on the crank 67 .

On the crankshaft 61, for example, an oil passage 82 through which lubricating oil supplied by an oil supply pump such as a trochoidal gear pump (Trocoroid Pump) can circulate is provided coaxially, and from this oil passage 82, the There are oil outlet holes 71, 72, 73 and 74 that supply lubricating oil to the positions that must be oiled at predetermined positions. As shown in Figure 8, on the outer peripheral surface of the crank 67, an oil groove 76 penetrating in the axial direction is provided, and the oil groove 76 and the oil groove 75 extending axially on the inner peripheral surface of the secondary bearing 65 form an oil outlet through the oil outlet. The passages for the lubricating oil in the holes 71, 72 lubricate the crank 67 and the secondary bearing 65.

Similarly, an oil groove 77 and an oil groove 78 are formed on the outer peripheral surface of the crank 66 and the inner peripheral surface of the main bearing 64 as channels for lubricating oil for lubricating the main bearing, so that the lubricating oil is introduced from the oil outlet holes 73 and 74, respectively.

For this horizontal rotary compressor, a hole 70 for the passage of the crankshaft 61 is provided on the partition plate 59 separating the two cylinders 62 and 63. Usually, considering the installation of the compression parts, the hole 70 must be made The bore diameter is greater than the diameters of the cranks 66 and 67. However, if you look at the main bearing 64 and compare the sealing width a of the end surface of the roller piston 68 and the contact portion of the main bearing 64 with the end surface of the other side of the roller piston 68 and the spacer. The sealing width b of the contact part of the plate 59, it can be found that the width b must be smaller than the width a, and the sealing performance at the width b will become worse. Therefore, the lubricating oil introduced from the oil outlet hole 73 of the crank 66 does not A small amount of oil flows through the holes 70 of the partition plate 59 and further leaks into the compression chamber. Therefore, there is a problem of insufficient lubrication on the side of the main bearing 64 . For the same reason, the problem of poor lubrication also occurs on the auxiliary bearing 65 .

Therefore, the object of the present invention is to provide a horizontal rotary compressor which eliminates the problems of the prior art, the lubricating oil can be well distributed on the bearing side and the oil supply can be improved. performance.

In order to achieve the above-mentioned purpose, the horizontal rotary compressor of the present invention includes: an electric motor installed in a closed casing; a compression component having a first cylinder and a second cylinder connected via a partition; and the crankshaft of the compression part supported by bearings; and an oil feed pump for forcibly supplying lubricating oil to the sliding surface of the compression part; An oil passage on the sliding surface of the compression member and an oil hole communicating with the oil passage; wherein an oil groove that guides the lubricating oil supplied through the oil hole to the bearing side is formed on the crank, the An oil groove terminates at a central position of the crank, and a seal portion is provided to restrict the flow of lubricating oil from the terminal end of the oil groove to the outer peripheral surface of the crank on the separator side.

In addition, the sealing portion may be formed of an oil groove having a flow cross-sectional area smaller than that of the oil groove, or the oil groove may be formed of a helical groove inclined with respect to the axial direction of the crankshaft.

According to the present invention, the lubricating oil sent to the oil groove of the crank cannot flow to the side of the separator because of the sealing portion, but flows to the side of the bearing, so that the phenomenon of poor lubrication of the bearing can be prevented. In addition, when the sealing part is an oil groove with a small flow cross section, flow resistance occurs due to the change of the flow cross section, and the lubricating oil is difficult to flow to the separator side, and most of the lubricating oil is supplied to the bearing. Moreover, when the oil groove is a helical groove inclined relative to the axial direction of the crankshaft, the lubricating oil in the oil groove is subjected to centrifugal force and flows to the bearing better.

An embodiment of the horizontal rotary compressor of the present invention will be described below with reference to the accompanying drawings.

Fig. 1 is a longitudinal sectional view showing an overall structure of an embodiment of a horizontal rotary compressor according to the present invention.

Fig. 2 is a sectional view showing a main part of a compression unit of a horizontal rotary compressor according to a first embodiment.

Fig. 3 is a plan view showing an oil groove of a crank of a crankshaft.

Fig. 4 is a plan view showing an oil groove of a crank of a crankshaft in a horizontal rotary compressor according to a second embodiment.

Fig. 5 is a plan view showing an oil groove of a crankshaft of a crankshaft in a horizontal rotary compressor according to a third embodiment.

Fig. 6 is a cross-sectional view showing main parts of a compression unit of a horizontal rotary compressor according to a fourth embodiment.

Fig. 7 is a sectional view showing main components of a compression unit of a conventional horizontal rotary compressor.

Fig. 8 is a plan view showing an oil groove on a crank of the crankshaft in the horizontal rotary compressor of Fig. 7 .

In FIG. 1, reference numeral 10 denotes a sealed casing, 11 denotes a motor, and 12 denotes a compression part. The motor 11 includes a stator 13 fixed to the inner peripheral surface of the sealed casing 10 and a rotor 14 embedded in the stator with a gap. A crankshaft 15 is connected concentrically within the rotor 14 , and the electric motor 11 and the compression element 12 are connected by the crankshaft 15 .

On the one hand, in the compression unit 12 , the first cylinder 16 and the second cylinder 17 are separated by a partition 18 and arranged continuously, and these components are integrally fixed to the inner peripheral surface of the sealed casing 10 by a bracket 19 . Moreover, while the motor room A and the machine room B are separated by the bracket 19 , the motor room A and the machine room B communicate with each other through the communication hole 19 a through the lower part of the bracket 19 and the first cylinder 16 .

The crankshaft 15 passes through the first cylinder 16 and the second cylinder 17 and is rotatably supported by a main bearing 20 and a sub bearing 21 on the first cylinder 16 side and the second cylinder 17 side.

On the crankshaft 15, eccentric cranks 22 and 23 are integrally provided with it, and in the cylinder chamber of the first cylinder 16, the crank 22 and the roller piston (ロ-ラ) 24 embedded thereon are arranged inside, Similarly, a crank 23 and a roller piston 25 are provided inside the cylinder chamber of the second cylinder 17 .

In addition, in the first cylinder 16 and the second cylinder 17, sliding pieces 26, 27 (not shown) are slidable in respective radial directions. These slide plates are all pressed toward the center of the cylinder by the elastic force of the compression springs 28,29. The sliding plates 26, 27 reciprocate with the eccentric rotation of the roller pistons 24, 25 integrally rotating with the crankshaft 15, so that the volume of the cylinder chamber changes periodically, and a compression cycle of suction, compression, and discharge is performed.

As a positive displacement oil pump for supplying lubricating oil to the main bearing 20 of the compression member 12 configured as above, the sub bearing 21, and the respective sliding surfaces of the roller pistons 24 and 25, a trochoidal gear pump (Trocoroid Pump) 30 can be used. .

The trochoidal gear pump 30 is mounted on the end of the sub-bearing 21 within the valve housing 52 . In this embodiment, as the trochoidal gear pump 30 , a known trochoidal gear pump including a large gear on the outside and a small gear meshing on the inside is used. The pinion is connected to the front end of the crankshaft 15 and rotates together with the crankshaft 15 . The lubricating oil sucked by the oil suction pipe 31 is pressurized due to the volume change of the space formed between the tooth surface of the large gear and the pinion gear, and the lubricating oil flows through the oil passage 32 formed in the axial direction of the crankshaft 15 through the The oil passage is supplied to the sliding surfaces of the main bearing 20, the sub bearing 21, the roller pistons 24 and 25, the slide plates 26 and 27, etc. to be lubricated.

2 is a cross-sectional view of the compression member 12 showing the oil passage through which lubricating oil flows, and FIG. 3 is a plan view showing the oil groove of the crank 23 on the crankshaft 15 .

On the crankshaft 15, an oil passage 32 for guiding the lubricating oil discharged from the trochoidal gear pump 30 is coaxially formed, and oil holes penetrating in the radial direction are pierced at predetermined positions sequentially from the sub-bearing 21 side with a certain gap. 33, 34, 35 and 36. In this case, the oil hole 33 is provided near the end surface of the auxiliary bearing 21 , and lubricating oil is led out from the oil groove 37 axially provided on the inner peripheral surface of the auxiliary bearing 21 . The oil hole 34 , as shown in FIG. 3 , is pierced at a side close to the partition plate 18 and communicates with an oil groove 38 axially provided on the outer peripheral surface of the crank 23 . In this embodiment, the oil groove 38 does not traverse the entire outer circumference of the crank 23 in the axial direction, but stops at a position so that the outer circumference of the crank 23 between the terminal end of the oil groove 38 and the separator 18 The portion with a length of 1 forms a closed portion 41 as a blocking member that restricts the flow of lubricating oil.

Similarly, an oil groove 39 is formed in the axial direction on the outer peripheral surface of the crank 22 , and an oil groove 40 serving as a lubricating oil passage is formed in the axial direction on the inner peripheral surface of the main bearing 20 . The oil hole 35 communicates with the terminal end of the dividing plate 18 side of the oil groove 39, because the oil groove 39 ends in the middle of the outer peripheral surface of the crank 22, and a portion with a length of 1 on the outer peripheral surface of the above-mentioned crank 23 is formed as a restriction. A closed portion 42 where lubricating oil flows. The oil hole 36 is pierced at a position close to the main bearing 20 , and lubricating oil is introduced into the oil groove 40 of the main bearing 20 through the oil hole 36 .

In addition, a hole 54 with a diameter larger than that of the cranks 22 and 23 is opened in the middle of the partition plate 18 separating the first cylinder 16 and the second cylinder 17. The purpose of this hole 54 is to install the compression parts. The crankshaft 15 can be passed through the bulkhead 18 .

Next, in Fig. 1, in the sealed casing 10, a suction pipe (not shown) is connected to one side of the mechanical chamber B, and a discharge pipe 50 is connected to one side of the motor chamber A. With such piping, the gas compressed in the cylinder chamber of the second cylinder 17 is discharged from the discharge valve 55 to the inside of the valve cover 52, and is discharged from the sub-bearing 21, the second cylinder 17, the partition plate 18, the first cylinder 16 and the gas passage (not shown) on the main bearing 20 leads to the motor chamber A by the valve cover 56 and the muffler 57 on the main bearing 20 side. Similarly, the gas compressed in the cylinder chamber of the first cylinder 16 is discharged from the discharge valve 58 on the side of the main bearing 20 , introduced into the motor chamber A through the valve cover 56 and the muffler 57 , and then discharged from the discharge pipe 50 .

The present embodiment is constituted in the above-mentioned manner, and its function will be described below.

During operation of the compressor, since the trochoidal gear pump 30 is driven with the rotation of the crankshaft 15 , lubricating oil sucked by the oil suction pipe 31 is pressurized and discharged into the oil passage 32 of the crankshaft 15 . In FIG. 2 , lubricating oil for lubricating the sub-bearing 21 enters the oil groove 37 through the oil hole 33 and is supplied to the sliding surface of the inner periphery of the sub-bearing 21 . In addition, the lubricating oil flowing into the oil groove 38 from the oil hole 34 on the crank 23 is difficult to flow to the partition plate 18 because of the obstruction of the sealing part 41, but flows to the auxiliary bearing 21 side through the oil groove 38, and merges with the oil introduced from the oil hole 33, thereby Played a good lubrication of the auxiliary bearing.

Likewise, the soil bearing 20 is lubricated by the oil flowing from the oil hole 36 into the oil groove 40 on the inner periphery of the main shaft bearing 20 . Also, as in the case of the sub-bearing 21, the oil introduced into the oil groove 39 from the oil hole 35 of the crank 22 flows from the oil groove 39 to the main bearing 20 instead of the separator 18 due to the blocking of the sealing portion 42.

Owing to must make crankshaft 15 pass dividing plate 18, so must be provided with a hole 54 on dividing plate 18 bigger than crank 22 and 23 external diameters, the seal width b of the respective end faces of roller piston 24 and 25 at dividing plate 18 side is because Relatively small, so that the seal is not very good. Therefore, in the past, the lubricating oil flowing to the side of the partition plate 18 would flow from the hole 54 to the compression chamber, causing poor lubrication in the main bearing 20 and the auxiliary bearing 21. It is difficult for oil to flow to the closed portions 41 and 42 of the separator 18, so that the previous disadvantages can be prevented.

Next, a second embodiment will be described with reference to FIG. 4 .

In this second embodiment, as the sealing part of the lubricating oil flowing into the oil groove 38 of the crank 23 of the crankshaft 15 and the oil groove 39 of the crank 22, it is an oil groove 43 and 44 with a smaller and narrower oil axial extension flow section. In this second embodiment, flow resistance occurs due to a change in the flow cross section, making it difficult for lubricating oil to flow toward the partition plate 18 side.

Next, a third embodiment will be described with reference to FIG. 5. FIG.

The oil grooves 38 and 39 of the cranks 23 and 22 of the above-mentioned embodiment are formed in the axial direction, but in this third embodiment, the oil grooves 45 and 46 are constituted by helical grooves inclined relative to the axial direction, respectively, as the sealing portion 41 and 42 are the same as the first embodiment of FIGS. 2 and 3 .

According to the third embodiment, when the crankshaft 15 rotates, the lubricating oil is subjected to centrifugal force, the centrifugal force acting in the direction of the radius. And since the oil grooves 45 and 46 are inclined relative to the axial direction, the lubricating oil flowing through the oil grooves 45 and 46 is well supplied to the side of the auxiliary bearing 21 and the main bearing 20 respectively.

Next, FIG. 6 shows a cross-sectional view of the structure of the compression member of the fourth embodiment.

In this fourth embodiment, the hole 54 formed on the partition 18 communicates with the internal storage oil pool of the sealed casing 10 through the oil passage 60, so that the opening on the inlet side of the oil passage 60 is immersed in the mechanical chamber B. In the lubricating oil stored in the side.

According to this fourth embodiment, during the operation of the compressor, the inside of the sealed casing 10 has a higher pressure because it is filled with compressed gas. low state. Due to the pressure difference, the lubricating oil stored at the bottom of the sealed casing 10 is sucked into the hole 54 through the oil passage 60 on the partition.

Therefore, lubricating oil seeps out from the hole 54 to supply the sliding contact surfaces of the partition plate 18 and the end faces of the roller pistons 24 and 25, and these end faces are sealed due to the lubricating oil.

As can be seen from the above description, because the outer peripheral surface of the crank of the crankshaft is provided with an oil groove that guides the lubricating oil supplied by the oil pump to the bearing side and a sealing portion that restricts the flow of lubricating oil to the separator, thereby eliminating the need for the lubricant to pass through the separator. The existing shortcomings of insufficient oil supply to the bearing caused by the leakage of the hole in the cylinder chamber can fully supply oil to the bearing, so that the reliability of the compressor is improved.

In addition, since the oil groove is formed of a helical groove inclined with respect to the axial direction of the crankshaft, the lubricating oil introduced into the oil groove is subjected to centrifugal force, thereby obtaining the effect of better oil supply to the bearing.

Claims (3)

1. A horizontal rotary compressor, comprising: a motor (11) installed in a closed casing (10); a first cylinder (16) and a second cylinder (17) connected via a dividing plate (18) ) of the compression part (12); has a crank (22, 23) connecting the motor (11) and the compression part (12) and is supported by a bearing (20, 21) crankshaft (15); and to the An oil feed pump (30) for forcibly supplying lubricating oil to the sliding surface of the compression member (12); inside the crankshaft (15) there is a device for guiding the lubricating oil supplied by the oil feed pump (30) to the compression member (12) The oil passage (32) on the sliding surface and the oil holes (34, 35) communicating with the oil passage (32); It is characterized by: Oil grooves (38, 39) for guiding the lubricating oil supplied through the oil holes (34, 35) to the side of the bearings (20, 21) are formed on the cranks (22, 23). (38, 39) end at the middle position of the crank (22, 23), and there is a crank (22, 23) that restricts lubricating oil from the terminal end of the oil groove (38, 39) to the side of the separator (16). ) The sealing part (41) of the outer peripheral surface flow. 2. The horizontal rotary compressor according to claim 1, characterized in that: the sealing part (41) also has a seal that communicates with the oil groove (38, 39) and is larger than the oil groove (38, 39). Oil grooves (43, 44) with a small flow cross-sectional area. 3. The horizontal rotary compressor according to claim 1, characterized in that the oil grooves (38, 39) are grooves inclined relative to the axial direction of the crankshaft (15).

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