JPH0988857A - Lubricating device of horizontal hermetic compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To feed the lubricating oil to the prescribed part to be lubricated without delay in starting a compressor by providing an oil feeding passage to directly connect an oil tank to a sliding part or a rolling part of a compression mechanism in a horizontal compressor provided with an enclosed housing in which the compression mechanism and a motor are and the oil tank. SOLUTION: In a horizontal enclosed compressor in which an enclosed housing 8 is connected to an oil tank 9 by a connection pipe 92, when the compressor is stopped for a long time or after the reversing operation of the liquid, a large volume of the refrigerant is dissolved in the lubricating oil in the oil tank 9. When the compressor is started in this condition, the pressure in the oil tank is also dropped due to the pressure drop in the enclosed housing 8. The foaming phenomenon that the refrigerant dissolved in the lubricating oil is foamed and boils occurs, and the pressure in the oil tank 9 is increased. As a result, the differential pressure is generated between in the oil tank 9 and in the enclosed housing 8, and this differential pressure allows the lubricating oil to be lubricated on a thrust surface 65 through an oil feed pipe 57, an oil feed hole 58, and an oil groove 66.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a lubricating device for a horizontal hermetic compressor for an air conditioner.

[0002]

2. Description of the Related Art FIG. 3 is a vertical sectional view of a conventional horizontal scroll compressor. In the figure, the inside of the closed housing 8 is partitioned by a discharge cover 31 into a high-voltage side 44 and a low-voltage side 45. Inside the low-pressure side 45, a scroll-type compression mechanism C is arranged in front of the low-pressure side 45, and an electric motor M is arranged in the rear thereof, which are interlockingly connected to each other via a rotary shaft 5. The electric motor M is a rotor M
The rotor Ma is fixed to the rotating shaft 5, and the stator Mb is fixed to the hermetic housing 8.

The scroll type compression mechanism C allows a fixed scroll 1, an orbiting scroll 2 and a revolving orbiting motion of the orbiting scroll 2 and prevents its rotation from rotating, such as an Oldham link, and the fixed scroll 1. And a frame 6 to which the electric motor M is fastened, a front bearing 71 and a rear bearing 72 that pivotally support the rotary shaft 5, and the like.

The fixed scroll 1 has an end plate 11 and a spiral wrap 12 provided upright on the inner surface of the end plate 11, and a discharge port 13 is provided at the center of the end plate 11.
The orbiting scroll 2 is provided with an end plate 21 and a spiral wrap 22 which is erected on the inner surface of the end plate 21, and a drive bush 54 is disposed in a boss 23 which is erected on the outer surface of the end plate 21 via a orbiting bearing 73. An eccentric pin 53 protruding from the end of the rotary shaft 5 is rotatably fitted in a hole 55 formed in the drive bush 54.
A plurality of closed spaces 24 are formed by eccentric the fixed scroll 1 and the orbiting scroll 2 with respect to each other by a predetermined distance and engaging them with each other while shifting the angle by 180 degrees.

The frame 6 is fixed to a hermetically sealed housing 8, and a thrust surface 65 formed on the front surface of the frame 6 and a back surface of the orbiting scroll 2 are in sliding contact with each other to cause a swirl caused by the internal pressure of the hermetically sealed space 24 during operation. Scroll 2
It supports the thrust load of. Further, an oil groove 66 is formed in the thrust surface 65.

An oil tank 9 is horizontally installed outside the lower side of the closed housing 8. The inside of the oil tank 9 is communicated with the inside of the closed housing 8 by a connecting pipe 92. A positive displacement oil pump 51 is attached to the rear end of the rotary shaft 5. A suction pipe 56 is connected to a suction port (not shown) of the oil pump 51, and a tip of the suction pipe 56 is open in the oil tank 9. Also,
A discharge port (not shown) of the pump 51 is communicated with an oil supply hole 52 formed in the rotary shaft 5.

When the electric motor M is driven to rotate, the rotary shaft 5, the eccentric pin 53, the drive bush 54, and the boss 23.
The orbiting scroll 2 is driven via a revolving orbiting mechanism composed of, for example, and the orbiting scroll 2 is revolved on a circular orbit having a revolution revolving radius while being prevented from rotating by a rotation inhibiting mechanism 3. Then, the refrigerant gas enters the low-pressure side 45 through the suction pipe 82, and this gas passes through the passage 61 and enters the low-pressure chamber 4.
After 3 times, it is sucked into the closed space 24. Then, as the volume of the sealed space 24 decreases due to the orbiting motion of the orbiting scroll 2, it reaches the central portion while being compressed,
The check valve 17 is pushed open from the discharge port 13 and the high pressure chamber 42 is opened.
To the high pressure side 44, and is discharged to the outside through the discharge pipe 83.

At the same time, the oil pump 51 is driven, the lubricating oil stored in the oil tank 9 is sucked up through the suction pipe 56, is urged by the oil pump 51, and is discharged to the oil supply hole 52. Further, this lubricating oil flows forward in the oil supply hole 52 and then splits midway to lubricate the rear bearing 72 and the front bearing 71, while the main stream is ejected from the opening of the oil supply hole 52 at the tip of the eccentric pin 53, and eccentric. Pin 53, slewing bearing 7
3 is lubricated and enters the oil sump chamber 63 formed between the orbiting scroll 2 and the frame 6.

Further, the lubricating oil passes through the oil groove 66 and lubricates the sliding portions such as the thrust surface 65 and the rotation preventing mechanism 3. Further, part of the lubricating oil that has entered the oil sump chamber 63 is part of the oil drain hole 62.
To the bottom of the closed housing 8. Then, the lubricating oil dripping on the inner bottom portion of the closed housing 8 passes through the connecting pipe 92 and enters the oil tank 9 where it is stored.

[0010]

In the above-mentioned conventional horizontal hermetic compressor, when the compressor is started, the sliding portion which is far from the oil pump 51, that is, the thrust face 65 on the rear face of the orbiting scroll 2 and the front face of the frame 6 is used. There will be a delay in the lubrication of the sliding parts such as. At the time of start-up in a normal operating state, no particular trouble occurs even if there is such a delay in refueling. However, when the compressor is stopped for a long period, or when the compressor is stopped after the liquid back operation, the thrust surface 65 is
The oil film is washed off by the refrigerant and becomes a completely dry state, which is a severe lubrication state against a delay in refueling.

Moreover, since a large amount of refrigerant is dissolved in the lubricating oil in the oil tank 9, when the compressor is started,
The oil pump 51 sucks the foamed refrigerant gas. For this reason, the pumping capacity of the oil pump 51 is reduced, and the above-mentioned oil supply delay becomes longer.

As described above, in the conventional compressor shown in FIG. 3, when the compressor is restarted after being stopped for a long time or after stopping the liquid back operation, the sliding portion in the compression mechanism C, especially the thrust surface 6
5 has a problem that seizure occurs due to delay in refueling.

An object of the present invention is to supply lubricating oil to a required lubrication section without delay at the time of starting the compressor, thereby minimizing the oil supply delay even when a large amount of refrigerant is dissolved in the lubricating oil. Shorten the length to prevent accidents such as seizure of sliding parts and rolling parts.

[0014]

DISCLOSURE OF THE INVENTION The present invention is to solve the above-mentioned problems, and the first means, which is the gist of the present invention, is to arrange a compression mechanism and a substantially horizontal position in the compression mechanism in a horizontally sealed housing. A motor for driving a compression mechanism, which is connected via a rotary shaft, is housed, and an oil pump driven by the rotary shaft, and a suction port and a suction pipe of the oil pump installed below the hermetically sealed housing are installed. In a lubrication device for a horizontal compressor having an oil tank communicated with the inside of the hermetic housing through a connecting pipe, the oil tank and the sliding portion or rolling portion of the compression mechanism are directly connected to each other. This is because the oil supply passage to be connected is provided.

According to the above means, when the compressor starts, the pressure in the hermetically sealed housing drops, and the pressure in the oil tank drops accordingly. In the case of starting after the stop for a long period of time or after the stop after the liquid back operation. Since a large amount of the refrigerant is dissolved in the lubricating oil in the oil tank, a foaming phenomenon (foaming phenomenon) in which the refrigerant becomes a bubble and boil occurs, and the pressure in the oil tank rises.

As a result, a pressure difference occurs between the pressure inside the oil tank and the pressure inside the closed housing. Due to this pressure difference, the lubricating oil in the oil tank is quickly sent to the sliding parts and rolling parts in the compression mechanism through the oil supply passage that directly connects the oil tank and the closed housing. There is no delay in refueling at startup.

The second means of the present invention is the check valve mechanism according to the first means, which shuts off the connecting pipe when the pressure in the closed housing in the connecting pipe falls below a certain pressure. Has been established.

According to the above means, when the compressor is started, the pressure in the hermetically-closed housing is lowered, whereby the check valve mechanism is closed, and the pressure difference between the pressure in the oil tank and the pressure in the hermetically-sealed housing is reduced. Occurs. Due to this pressure difference, the lubricating oil in the oil tank is forcibly sent directly to the sliding portion in the compression mechanism through the oil supply passage as in the case of the first means.
At the same time, the pressure difference causes the lubricating oil in the oil tank to be forced into the oil pump through the suction pipe.

In this case, since the check valve mechanism forcibly causes the pressure difference, the fuel can be supplied more quickly and reliably than the first means. The check valve mechanism is preferably a spherical valve type including a spherical valve body. This makes the structure of the check valve mechanism simple and compact.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described in detail below with reference to the drawings. FIG. 1 shows a cross-sectional view of a horizontal hermetic compressor for an air conditioner according to an embodiment of the present invention.

In FIG. 1, C is a scroll type compression mechanism, 1 is a fixed scroll of the compression mechanism C, 2 is an orbiting scroll, and 3 is a rotation preventing mechanism. M is an electric motor for driving the compression mechanism C, 5 is a rotary shaft that connects the compression mechanism C and the electric motor M, 8 is a hermetic housing, and 6 is a frame.

Reference numeral 51 is an oil pump mounted on the shaft end of the rotary shaft 5, 9 is a lubricating oil tank, and 56 is the oil pump 51.
Is a suction pipe that connects the suction port of and the lubricating oil tank 9.
Reference numeral 92 is a connecting pipe that connects the lower portion of the closed housing 8 and the oil tank 9. Reference numeral 66 denotes an oil groove formed on the end surface of the frame 6, that is, the thrust surface 65, which is in sliding contact with the orbiting scroll 2.

Reference numeral 58 is an oil supply hole formed in the frame 6, one end of which is opened in an oil groove 66 formed in the thrust surface 65 formed on the front surface of the frame 6, and the other end is hermetically sealed. It is extended to the outside of the housing 8 and is connected to an oil supply pipe 57 additionally provided in the oil tank 9. Same refueling pipe 57
The other end of is open in the oil tank 9.

The other structure is the same as that of the conventional one shown in FIG. 3, and the same members as those shown in FIG.

In the compressor configured as described above,
Oil tank 9 when stopped for a long time or after a liquid back operation
A large amount of refrigerant is dissolved in the lubricating oil inside, but when the compressor C is started in this state, the pressure in the sealed housing 8 drops, so that the pressure in the oil tank 9 communicating with the housing 8 also drops. . As a result, a so-called foaming phenomenon (foaming phenomenon) occurs in which the refrigerant dissolved in the lubricating oil becomes a bubble and boils, and the internal pressure of the oil tank 9 rises. As a result, a pressure difference is generated between the inside of the oil tank 9 and the inside of the closed housing 8, and this pressure difference causes the lubricating oil in the oil tank 9 to pass through the oil supply pipe 57, the oil supply hole 58, the oil groove 66, and the thrust surface 6
It is sent to No. 5, and it is lubricated. As described above, even when the engine is started from a state in which a large amount of the refrigerant is dissolved in the lubricating oil, such as when the liquid is stopped for a long period of time or when the liquid bag is stopped, the thrust surface 65 is
Will be quickly supplied with a sufficient amount of lubricating oil,
The occurrence of seizure is prevented.

FIG. 2 shows a second embodiment of the present invention. In this embodiment, the check valve mechanism 10 is attached to the connecting pipe 92 for returning the oil between the closed housing 8 and the oil tank 9.
0 is provided.

That is, referring to FIG. 2, the check valve mechanism 100 is shown.
Is a retainer 10 having a valve seat 102 and a large number of through holes.
3 is formed by inserting the spherical valve element 101 into the valve chamber 106 between the valve chamber 3 and the valve chamber 106, and is provided near the opening of the connecting pipe 92 on the hermetic housing 8 side. It should be noted that the check valve mechanism 100 can be installed in any portion of the connecting conduit 92. Except for the above configuration, it is the same as the first embodiment shown in FIG.

When the compressor C having the check valve mechanism 100 shown in FIG. 2 is stopped for a long time and then started, the oil pump 51 is rotated and the gas in the hermetic housing 8 is compressed by the compression mechanism C. Since the air is sucked into the closed space 24, the pressure in the closed housing 8 starts to drop.

On the other hand, since the pressure in the oil tank 9 is the same as when the compression mechanism C is stopped, there is a pressure difference between the pressure in the closed housing 8 and the pressure in the oil tank 9. Due to this pressure difference, the gas in the oil tank 9 flows back into the closed housing 8 through the inside of the connecting pipe 92, and the valve body 101 of the check valve mechanism 100 is lifted by this gas flow and the valve seat 10 is opened.
The second gas passage 104 is closed. As a result, the pressure difference between the pressure in the closed housing 8 and the pressure in the oil tank 9 increases, and the pressure difference causes the lubricating oil in the oil tank 9 to pass through the oil supply pipe 57 and the oil supply hole 58 and further to the oil groove 66. Then, it is sent to the thrust surface 65 via.

In the first embodiment shown in FIG. 1, the thrust surface 65 is refueled by the pressure difference that naturally occurs between the closed housing 8 and the oil tank 9. By the action of the above, the connecting pipe is closed and the pressure difference is forcibly produced, so that the fuel can be supplied more quickly and surely than in the first embodiment.

In addition to the above, the check valve mechanism 100 has the following function of preventing the deterioration of the capacity of the oil pump. That is, due to the pressure difference between the oil tank 9 and the closed housing 8, the lubricating oil stored in the oil tank 9 passes through the suction pipe 56 and the oil pump 5 even if a large amount of refrigerant is dissolved therein.
It is forcibly sent into the inside of No. 1 and is urged by the oil pump 51 to be supplied to the required lubrication point. Therefore, the oil pump 51 operates reliably even at the time of start-up, and there is no reduction in capacity.

Further, when the internal pressure of the oil tank 9 decreases due to the decrease in the amount of lubricating oil in the oil tank 9, the valve body 101 of the check valve mechanism 100 falls by its own weight and opens the gas passage 104, It is held on the retainer 103. As a result, the lubricating oil that has dripped at the bottom of the closed housing 8 will not allow the communication port 10 of the valve seat 102 of the check valve mechanism 100.
4, passing through many holes 105 of retainer 103, connecting pipe 9
After passing through 2, the oil enters the oil tank 9 and is stored therein.

[0033]

The present invention is configured as described above.
According to the first aspect of the present invention, when the compressor is activated, the pressure in the oil tank increases due to the pressure increase in the oil tank caused by the foaming phenomenon (forming phenomenon) of the refrigerant dissolved in the lubricating oil in the oil tank. A pressure difference is generated between the inside of the closed housing and the lubricating oil in the oil tank is directly sent to the sliding portion and the rolling portion in the compression mechanism through the oil supply passage.

As a result, after the compressor has been stopped for a long period of time or after stopping after the liquid back operation, the thrust surface and other oil films on the sliding parts and rolling parts in the compression mechanism are washed off by the refrigerant to be completely dry. Even if it is, the lubricating oil can be quickly sent to the sliding portion and the rolling portion when the compressor is started, so that an accident such as seizure can be prevented.

Further, according to the second aspect of the present invention, when the compressor is started, the pressure difference between the oil tank inside and the closed housing caused by the closing of the check valve mechanism prevents the lubricating oil inside the oil tank. At the same time as being sent directly to the sliding part and rolling part of the compression mechanism through the oil supply passage, it is forcibly sent into the oil pump through the suction pipe due to the pressure difference. The pressure difference is forcibly generated by closing the connecting pipe with a check valve mechanism.
It is possible to obtain a larger pressure difference than in the above case, and it is possible to realize reliable and quick refueling.

In addition, after the compressor has been stopped for a long time,
Even if a large amount of refrigerant is dissolved in the lubricating oil such as after the stop after the liquid back operation, the lubricating oil can be sent to the oil pump, and the deterioration of the pump performance can be prevented. As a result, the delay of refueling can be further shortened and the above effects can be synergistically ensured.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view of a horizontal hermetic compressor according to a first embodiment of the present invention.

FIG. 2 is a partial sectional view showing a main part of a second embodiment of the present invention.

FIG. 3 is a vertical sectional view of a conventional horizontal hermetic compressor.

[Explanation of symbols]

 C compression mechanism M electric motor 5 rotating shaft 8 hermetic housing 9 oil tank 51 oil pump 52 oil supply hole 56 suction pipe 57 oil supply pipe 58 oil supply hole 92 connecting pipe 100 check valve mechanism

Claims (2)

[Claims] 1. A compression mechanism and a motor for driving a compression mechanism, which is connected to the compression mechanism via a rotary shaft arranged substantially horizontally, are housed in a horizontally sealed housing; and the motor is driven by the rotary shaft. Horizontal compressor provided with an oil pump, and an oil tank installed below the hermetic housing and communicating with the suction port of the pump via a suction pipe and with the interior of the hermetic housing via a connecting pipe. 3. A lubrication device for a horizontal hermetic compressor, characterized in that an oil supply passage for directly connecting the oil tank and the sliding portion or rolling portion of the compression mechanism is provided. 2. The lubricating device for a horizontal hermetic compressor according to claim 1, wherein a check valve mechanism is provided in the connecting pipe to shut off the connecting pipe when the pressure in the hermetic housing falls below a certain pressure. .