KR0128367B1 - Hirizontal rotary compressor - Google Patents

Abstract

The present invention relates to a two-cylinder type lateral rotary type that enables stable and sufficient oil supply from the ultra low speed region to the high speed region, and includes a first blade 27 accommodated in the first cylinder 16 and the second cylinder 17. The first blade chamber 32 and the second blade chamber 34 are respectively partitioned on the rear surface of the two blades 28 through the partition plate 28, and an oil supply path for introducing lubricating oil is provided in the blade chamber 32 of each cylinder. It is characterized in that the oil supply passages are formed independently so as to communicate with each other, and the oil supply passages are led out to the ends of the sub-axial bearings 21 and connected to each other.

Description

Horizontal rotary compressor

1 is a cross-sectional view showing an embodiment of a horizontal rotary compressor according to the present invention, a longitudinal section along the line I-I in FIG.

2 is an assembly view of components constituting the compression unit of the horizontal rotary compressor according to the embodiment.

3 is a perspective view showing the blade chamber of each cylinder in the compression section of the horizontal rotary compressor according to the embodiment.

4 is a cross-sectional view of the compression section showing the connection to the sub-bearing end of the oil feed pipe.

5 is a front view of the compression section showing the connection to the sub-bearing end of the oil supply pipe.

6 is a longitudinal sectional view along the VI-VI line of the horizontal rotary compressor of FIG.

7 is a perspective view showing the connection between the oil supply pipe and the oil supply cover to the sub-bearing end.

8 is a perspective view showing a connection between an oil supply pipe and a pipe holder on the cylinder side.

9 is a cross-sectional view showing the assembly state of the oil supply pipe, the pipe holder, the oil supply cover.

10 is a longitudinal sectional view of a conventional horizontal rotary compressor in which a blade of each cylinder is configured as a blade pump.

* Explanation of symbols for main parts of the drawings

10: hermetic casing, 11: electric motor part,

12: compression part, 15: crankshaft,

16: the first cylinder, 17: the second cylinder,

18: partition plate, 20: main bearing,

21: buoy bearing, 27: the first blade,

28: 2nd blade, 32: 1st blade room,

34: second blade chamber, 40: pipe holder,

41: first oil supply pipe, 42: second oil supply pipe,

45,60: oil supply cover, 49: nozzle,

77: discharge cover

The present invention relates to a two-cylinder type horizontal rotary compressor, and more particularly, to a horizontal rotary compressor comprising a blade of each cylinder as an oil supply pump.

In the conventional horizontal rotary compressor, various oil supply mechanisms such as oil supply mechanisms for supplying lubricating oil to the sliding part of the compression section, blade pump type with a function of oil supply pump to the blade, gear pumps, and centrifugal pumps are used. It is adopted.

In the so-called twin rotary compressor, in which a compression unit is formed by connecting a partition plate between two cylinders, a blade of one cylinder is used as an oil supply pump, and each blade of each cylinder is used together as a blade pump to increase the lubrication flow rate. It is known.

The compressor which supplies the lubricating oil discharged from the blade pump as a conventional technique regarding such an oil supply mechanism through the oil supply path provided in the partition plate of a cylinder is known (Japanese Patent Laid-Open No. 63-169921). The configuration of Fig. 10 is shown. Reference numeral 90 denotes a closed casing, 91 an electric motor portion, and 92 a compression portion. Reference numeral 93 denotes a crankshaft connecting the motor unit 91 and the compression unit, and the compression unit 92 is a first cylinder 97 divided between the main bearing 94, the sub-bearing 95 and the partition plate 96. And a second cylinder 98. In the conventional oil supply mechanism, the oil supply path 99 of the partition plate 96 is used as a common oil supply, and the first blade 100 and the second blade 10 are pumped by the reciprocating motion of the first blade. Lubricant is supplied to each sliding part of each of the cylinder 97, the main bearing 94, the second cylinder 98, and the sub bearing 95.

In recent years, however, inverter control has been used to change the rotational speed of a compressor from a low speed range to a high speed range. Therefore, it is important to ensure a stable supply of lubricating oil in response to a wide range of rotational speeds for the compressor oil supply mechanism.

However, in the conventional horizontal rotary compressor, the blade 100 of the first cylinder 97 is different because the two eccentric parts 102 and 103 have a phase difference of 180 ° in order to reduce vibration during rotation of the crankshaft 93. There is a phase difference of 180 ° with respect to the bladder 101 on the side. Therefore, when one blade pump is in the discharge stroke, the phases are opposite to each other as the other bladder pump is in the suction stroke, so when the oil passage 99 of the partition plate 96 is used in common, the flow of lubricating oil is As a result of the interference, a decrease in fueling efficiency can be found. In particular, in the low speed region, especially in the ultra low speed region, the reduction of the oil supply is a limitation of the operation.

Therefore, an object of the present invention is to solve the problems of the prior art and to provide a horizontal rotary compressor that enables stable and sufficient oil supply from the ultra low speed region to the high speed region.

In order to achieve the above object, according to the present invention, there is provided a compression unit having an electric motor unit installed in an airtight casing, a first cylinder and a second cylinder installed in the airtight casing and partitioned through a partition plate, and integrated with a rotating shaft of the motor unit. A crankshaft, first and second rollers respectively installed in the first cylinder and the second cylinder and pivoted by a phase difference of 180 degrees by the crankshaft, and abutting the first roller and the second roller, respectively. The first blade chamber and the second blade chamber accommodating the blades operated in phase difference of Fig., And the first blade chamber and the second blade chamber by lubricating oil by the reciprocating motion of the blade by the lubricating oil to the cylinder to the cylinder In the horizontal rotary compressor having a lubrication mechanism for lubricating sliding parts such as a roller and a crank shaft, the lubrication mechanism A first oil supply pipe communicating with the first blade chamber through an oil supply passage through one side of the second cylinder and the partition plate, a second oil supply pipe communicating with the second blade chamber, and the crank shaft. And an oil chamber provided at the end and communicating with the other side of the first oil supply pipe and the second oil supply pipe, and a passage formed coaxially in the crankshaft communicating with the sliding part in the oil chamber.

In the above-described configuration, the oil supply passage includes a first oil supply pipe and a second oil supply pipe in which an end of the inlet side is fixed to the second cylinder of the sub-bearing shaft through a pipe holder, and the first oil supply pipe is a second cylinder, The second oil supply pipe may be configured to communicate with the blade chamber of the second cylinder while communicating with the blade chamber of the second cylinder through a passage through the partition plate.

In addition, the outlet end portions of the first oil supply pipe and the second oil supply pipe are connected to the oil supply cover attached to the sub-bearing, and a passage for introducing oil from the oil chamber inside the oil supply cover is coaxially formed on the crankshaft. The impeller can be fitted.

As each blade is raised, oil is sucked into the blade chamber and compressed by the lowering of the blade. Since each blade chamber is partitioned by the partition plate and communicates with each other, the discharged oil is supplied to each sliding part of the compression part which requires oil supply in an independent oil supply circuit, thereby constituting a large capacity blade pump.

In addition, by setting the phase difference of 180 ° between the blades, the total volume of the combined blade chambers of both cylinders does not change depending on the relative movement of the blades, so that the discharged flow rate becomes constant at the same rotational speed and enables stable lubrication. When oil is supplied, each sliding part of the compression part that requires lubrication is forcibly supplied with an impeller of an oil passage installed coaxially with the crankshaft.

By passing the oil compressed by the blade through the nozzle having a small pipe diameter, the flow rate of oil flowing through the inside of the first oil supply pipe and the second oil supply pipe increases, so that the oil from the outside of the pipe is sucked into the pipe. The flow rate sucked and supplied increases.

Hereinafter, an embodiment of a rotary compressor according to the present invention will be described with reference to the accompanying drawings.

1 is a cross-sectional view of the entire horizontal rotary compressor according to the present embodiment, and is a longitudinal cross-sectional view along the line I-I of FIG.

Reference numeral 10 denotes a hermetic casing, 11 an electric motor portion, and 12 a compression portion. The motor unit 11 is composed of a stator 13 fixed to the inner circumferential surface of the hermetic casing 10 and a rotor 14 fitted to the inner side of the stator 13 so as to be movable. The crankshaft 15 is joined to the rotor 14, and the electric motor part 11 and the compression part 12 are connected by this crankshaft 15.

On the other hand, in the compression section 12, the first cylinder 16 and the second cylinder 17 are overlapped and installed through the partition plate 18, and at the same time, they are integrally sealed by the frame member 19 ( It is fixed to the inner peripheral surface of 10).

The motor chamber A and the machine chamber B are partitioned by the frame member 19, and the connection between the motor chamber A and the machine chamber B is formed through the lower portion of the frame member 19. Communicate through. The crankshaft 15 is inserted through the first cylinder 16 and the second cylinder 17, and at the same time, the main bearing 20 and the second cylinder 17 are attached to one side of each of the first cylinder 16 and the second cylinder l7. The bearing 21 is rotatably supported.

In addition, the crankshaft 15 is provided with an eccentric first crank part 23 and a second crank part 24, and the cylinder chamber of the first cylinder 16 is fitted to the first crank part 23 and the outside thereof. The first roller 25 is accommodated, and the second crank portion 24 and the second roller 26 are housed in the cylinder chamber of the second cylinder 17.

FIG. 2 is an assembly view showing the components constituting the compression unit 12, and FIG. 3 is a view showing the first cylinder 16, the second cylinder 17 and the partition plate 18 in detail. A first blade groove 31 and a second blade groove 33 are formed in the first cylinder 16 and the second cylinder 17, respectively. The first blade 27 is fitted into the first blade groove 31, and the second blade 28 is fitted into the second blade groove 33 so as to slide freely in the radial direction of the cylinder. These first blades 27 and the second blades 28 are applied together by the elastic force of the compression springs 29 and 30 toward the center of the cylinder, and the phase of the reciprocating motion is first crank part 23 of the crankshaft. ), The second crank portion 24 is set to be offset by approximately 180 ° in response to the eccentric phase.

In this way, each blade of the 1st blade 27 and the 2nd blade 28 comprises the blade pump mechanism using the reciprocating motion. That is, the first blade grooves 32 and the second blade grooves 32 of the first cylinder 16 and the second blade grooves 32 of the second cylinder 17 are respectively formed on the rear side of the blade. The blade blades 34 and the first blade chamber 32 and the second blade chamber 34 are partitioned as independent spaces which are not communicated with each other by the partition plate 18. In addition, the oil supply passages for introducing the lubricating oil sent to the sliding portions of the compression section 12 are configured as follows so as to communicate with the first blade chamber 32 and the second blade chamber 34 independently of each other.

In the present embodiment, as shown in FIGS. 3 and 6, the small cylinder holes 35 and 36 and the first cylinder 16 formed through the second cylinder 17 and the partition plate 18 are formed. A spot faciong 37 forms a passage communicating with the first blade chamber 32 in an assembled state, and the passage and the first oil supply pipe 41 constitute a passage for introducing lubricating oil. Moreover, the oil supply passage which connects to the 2nd blade chamber 34 continuously is formed using the 2nd supply pipe 42. As shown in FIG.

As shown in FIG. 4 and FIG. 5, the inlet side edge part of the 1st oil supply pipe 41 and the 2nd oil supply pipe 42 is supplied to the oil supply pipe 1 with respect to the 2nd cylinder 17 by the pipe holder 40. As shown in FIG. And 42 are positioned, respectively, and are connected to the oil supply cover 45 through the nozzle 49 which is smaller than the oil supply pipes 41 and 42 and becomes a connection pipe. The oil supply cover 45 on the side of the cylinder has communication holes 43 and 44 opened at positions facing the second blade groove 33 and the small diameter hole 35 of the second cylinder 17 (see FIG. 2). ) Is installed.

8 and 9 show the connection structure of the oil supply pipes 41 and 42, and FIG. 9 shows the cross section along the line A-A.

In the present embodiment, the outer periphery of the pipe end of the first oil supply pipe 41 and the second oil supply pipe 42 is formed with a projection 46 wound around the projection portion of the pipe holder 40 on the projection 46 ( The first oil supply pipe 41 and the second oil supply pipe 42 are held so that the 48 is engaged. The first oil supply pipe 41 and the second oil supply pipe 42 are fitted to the nozzle 49, respectively, and the passage 49a in the nozzle 49 is compressed with a small inner circumferential diameter on the oil supply pipe side. In addition, the nozzle 49 is fixed to the shoulder portion 50 of the oil supply cover 45 while the flange 49b is caught by the shoulder portion 50 of the oil supply cover 45. It joins by becoming.

On the other hand, the front end of the 1st oil supply pipe 41 and the 2nd oil supply pipe 42 is connected to the oil supply cover 60 attached to the sub bearing 21 side, respectively. As shown in FIG. 4 and FIG. 7, the first oil supply pipe 41 and the second oil supply pipe 42 protrude from the periphery of the connector 61 formed by protruding to the outside of the oil supply cover 60. The positioning of the pipe end by the latch 62 and the end of the tube on the inner circumferential surface of the connection port 61 from the outside may be performed.

In addition, in FIG. 8, the code | symbol 63 shows the oil suction port provided in the 1st oil supply pipe 41 and the 2nd oil supply pipe 42, respectively, in the vicinity of the nozzle 49, and as shown in FIG. As the first blade 27 and the second blade 28 are raised, oil is sucked into the first blade chamber 32 and the second blade chamber 34 from the oil suction hole 63.

In FIG. 1, FIG. 2, and FIG. 4, the oil supply cover 60 is the structure by which the valve cover 64 is hold | maintained whole. In this case, oil from the first oil supply pipe 41 and the second oil supply pipe 42 is confined to the oil chamber 65 inside the oil supply cover 60 and coaxial to the crank shaft 15 in the oil chamber 65. The impeller 66 fitted into the passage formed by the oil is forcibly lubricated through the oil holes 67a to 67d opening to the respective sliding surfaces of the compression section. A thruster plate 69 is fitted between the oil supply cover 60 and the sub-bearing 21 to restrict the shaft end surface of the crankshaft 15 through the plate holder 68.

On the other hand, the valve cover 64 is fixed to the sub-bearing 21 by the bolt 76, and the packing member 70 is mounted and hermetically sealed between the valve cover 64 and the oil supply cover 60. The space portion 71 inside the valve cover 64 has a high pressure gas discharged from the discharge valve 72 and becomes a high pressure, but the packing member 70 has a valve cover 64. The high pressure gas leaks from the machine chamber B from the interval between the oil supply cover 60 and the oil supply cover 60, thereby preventing the oil level from being lowered due to the disturbance of the pressure balance between the motor chamber A and the machine chamber B.

Next, in FIG. 1, in the closed casing 10, the discharge pipe connection part 76 is provided in the motor chamber A side, and the discharge pipe 77 is connected here. This discharge pipe 7 communicates with the machine room B via the discharge pipe contact portion 78 on the machine room B side.

The gas compressed in the second cylinder 17 is discharged from the discharge valve 72 to the space portion 71 of the valve cover 64 and perforated in the sub-bearing 21, the partition plate 18, and the main bearing 20. The gas passages 80, 81, 82, 83 (see FIG. 2) are discharged through the muffler 84 to the motor chamber A, and then led to the discharge tube 77. In addition, the gas compressed in the first cylinder 16 is discharged to the discharge chamber 88 by being discharged to the motor chamber A from the inside of the discharge valve 88 and the muffler 84. At this time, a suction action (discharger effect) occurs on the machine chamber B side through the discharge tube connecting portion 78 due to the flow of the high pressure gas flowing through the discharge tube 77 at the same time. The pressure becomes relatively low. For this reason, the oil of the motor chamber A side flows into the machine room B through the connection hole 19a which is perforated in the lower part from the frame member 19, and the oil oil level of the machine room B is ensured high. .

In Fig. 5, reference numeral 74 denotes a strainer and 75 denotes a suction pipe.

This embodiment is configured as follows and the operation thereof will be described next. Rotation of the crankshaft 15 during operation of the compressor causes the first cylinder 16, the first blade 27 of the second cylinder 17, and the second blade 28 to reciprocate and the first cylinder 16 ), The volume of the cylinder chamber inside the second cylinder 17 changes periodically, and the gas suction and compression discharge cycles are repeated.

In addition, in FIG. 6, when the first blade 27 is raised, the oil stored at the bottom of the airtight casing 10 passes through the nozzle 49 and the small diameter at the oil suction hole 63 of the first oil supply pipe 41. It is sucked into the first blade chamber 32 through the holes 34 and 36 and the spot facing 37. When the first blade 27 is lowered, the extruded oil is introduced into the oil chamber 65 from the first oil supply pipe 41 through the spot facing 37 and the small diameter holes 36 and 35, and also the impeller 66. The forcing is efficiently supplied to each sliding portion through the oil holes 67a to 67d. In this embodiment, since the nozzle 49 is connected to the inlet side of the first oil supply pipe 41 and the oil is ejected from the nozzle 49 to increase the flow rate of oil, the oil suction hole 63 is connected to the first. Since the oil is sucked into the oil supply pipe 41 and is sucked to increase the flow rate flowing through the first oil supply pipe 41, the flow rate supplied to each sliding part can be sufficiently secured.

In addition, in FIG. 1, the oil sucked into the second blade chamber 34 when the second blade 28 is raised is also lowered from the second blade 28 with the second oil supply pipe 42 at the nozzle 49. ) Is discharged and introduced into the second oil supply pipe (42) while supplying oil into the pipe from the oil suction hole (63) and is supplied to each sliding portion.

Thus, each blade pump mechanism is constituted in the first cylinder 16 and the second cylinder 17, and the first blade chamber 32 and the second blade chamber 34 are partitioned by partition plates 18, respectively. Since oil supply paths for introducing lubricant are independently installed, a large-capacity blade pump using two cylinder blades can be configured. For this reason, even if it is rotating at low speed, sufficient quantity of oil can be replenished.

In addition, the blade movement of the first cylinder 16 and the second cylinder 17 has a phase difference, and in the embodiment, the phase difference of about 180 ° is set so that the blade chambers 32 and 34 of both cylinders may be changed depending on the relative motion of the blades. Since the total space area does not change, the discharged flow rate becomes constant at the same rotation speed, and stable oil supply is possible.

As described above, according to the present invention, an oil supply passage for partitioning each blade chamber through a partition plate on the back of the blades accommodated in the first cylinder and the second cylinder and introducing lubricant oil is connected to the blade chamber of each cylinder. The oil supply passages are formed independently so as to communicate with each other, and the oil supply passages are led to the sub-bearing ends. For this reason, a large-capacity oil supply pump using each cylinder blade can be constituted, and the necessary oil supply amount can be ensured even in operation in a low speed region.

In addition, by providing a phase difference of about 180 ° between the blades of the first cylinder and the blades of the second cylinder, the total space volume combined with the respective blade rear space portions does not change by the relative operation of the blades, so that stable oil supply can be performed.

In addition, since the oil is forcibly supplied to each sliding part of the compression part requiring lubrication by an impeller in a flow path installed coaxially to the crankshaft, the lubrication effect can be enhanced.

In addition, the oil extruded by the blades is passed through the nozzle so that the oil from the outside of the pipe enters and is sucked into the inside of the pipe from the oil suction hole, thereby ensuring sufficient oil supply.

In addition, since the first oil supply pipe communicates with the first blade chamber through the oil supply passage passing through the second cylinder and the partition plate, processing is easy because the vertical partition hole is not required in the partition plate.

Claims (3)

A crankshaft integral with the rotating shaft of the motor, the first cylinder and the second cylinder installed in the hermetic casing, the first cylinder and the second cylinder which are partitioned and connected through the partition plate, the crankshaft integrated with the rotating shaft of the motor, and the first cylinder; A first roller and a second roller installed in a second cylinder and pivoted by a phase difference of 180 degrees by the crankshaft, and receiving blades which abut against the first roller and the second roller and operate at a phase difference of 180 degrees, respectively. By lubricating the first blade chamber and the second blade chamber and the first blade chamber and the second blade chamber by lubricating oil, the lubricating oil is pumped by the reciprocating motion of the blade to the sliding parts such as the cylinder, the roller and the crankshaft. In a horizontal rotary compressor having an oil supply mechanism for supplying oil, the oil supply mechanism has one end penetrating the second cylinder and the partition plate. A first oil supply pipe communicating with the first blade chamber through a flow path, a second oil supply pipe with one end communicating with the second blade chamber, and an end of the crankshaft installed at the end of the crankshaft; And an oil chamber communicating with the other end of the oil pipe, and a passage formed coaxially in the crank shaft communicating with the sliding portion in the oil chamber. A nozzle having a tube diameter smaller than that of the oil supply pipe is connected to one end of the first oil supply pipe and the second oil supply pipe communicating with the blade chamber, and an oil suction hole is formed in the vicinity of the nozzle. Horizontal rotary compressor, characterized in that. The horizontal rotary compressor according to claim 1 or 2, wherein an impeller is fitted into a passage coaxially formed in the crankshaft.