JPH0826861B2 - Scroll gas compressor - Google Patents

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll gas compressor, and more particularly to back pressure control for an orbiting scroll.

[0002]

2. Description of the Related Art In recent years, scroll compressors which have been put into practical use with the development of machine tools and which have attracted attention as compressors having low vibration and low noise characteristics are disclosed in, for example, Japanese Unexamined Patent Publication No.
As shown in Japanese Patent No. 49386, the suction chamber is provided at the outer periphery, and the discharge port is provided at the center of the spiral.
It is generally well known that the flow of compressed fluid is unidirectional, so that the fluid resistance during high-speed operation is small and the compression efficiency is high. Further, a compressor having a high-pressure gas closed shell structure of this kind has a structure shown in FIG. 5 as known from Japanese Patent Laid-Open No. 59-49386 or a structure shown in Japanese Patent Laid-Open No. 55-148994. 6 or the structure of JP-A-57-68579 in which the compressor of JP-A-55-178994 is turned upside down is proposed, and the back pressure chamber of the orbiting scroll is proposed. Lubrication of each sliding portion was configured as follows while reducing the axial thrust force acting on the orbiting scroll by appropriately setting the pressure.

That is, in FIG. 5, the fixed scroll wrap 123 supports the drive shaft 105 and the main body frame 1
02 is fixed to the end plate 121, the orbiting scroll wrap 116 is fixed to the wrap support disk 115,
The lap support disk 115 is arranged in a loose fit state in the back pressure chamber 120 between the end plate 121 and the main body frame 102 with a minute gap in the axial direction, and the back pressure chamber 120 is located outside the back pressure chamber.
A120a and the inner back pressure chamber B120b partition function
And, it is pivotally supported by an Oldham ring 118 having a rotation preventing function, and is pivoted by a driving motor 110 and a drive shaft 105 having an eccentric portion at its end. The inhaled / compressed gas is sealed shell 10
Discharge into 1. The lubricating oil separated from the discharge gas is collected in the oil sump 109 at the bottom of the closed shell 101, and the drive shaft 10
5, an oil hole 106 opened at the lower end of
And, through the bearing portion that supports the drive shaft 105, it is guided to the back pressure chamber 120 in a high pressure state by utilizing the centrifugal pump action. Further, the lubricating oil , which has been reduced in pressure to an intermediate pressure between the discharge pressure and the suction pressure through a minute gap in the sliding portion of the Oldham ring 118 , flows into the back pressure chamber A 120a, and then the balance passage 126 of the fine hole provided in the end plate 121. The sliding portions are lubricated in the process of flowing into the suction chamber 122 through the through holes.

Further, in FIG. 6, the back pressure chamber 220 is not partitioned by the Oldham ring 218 in terms of pressure.
There is no communication with the suction chamber 222, but a fine hole balance passage 226 provided in the lap support disk 215 of the orbiting scroll.
Is connected to the compression chamber 240 at an appropriate position by
The balance passage 226 opens and closes communication with the compression chamber 240 as the lap support disk 215 pivots, and constitutes intermittent oil supply between the back pressure chamber 220 and the compression chamber 240. The back pressure chamber 220, the drive shaft and the oil reservoir 209 at the bottom of the sealed shell 201 filled with ejection outlet gas 20
5 is communicated with the oil hole 206 provided in the No. 5 via a minute gap of the bearing that supports the drive shaft 205, and
Lubricating oil flows into the back pressure chamber 220 at an intermediate pressure and then balances.
Each slide in the process of flowing into the compression chamber 240 through the passage 226.
The moving part is refueled.

[0005]

However, in the structure having only the fine hole communication oil supply passage from the back pressure chamber 120 to the suction chamber 122 as shown in FIG. 5, the scroll compressor is incorporated into the heat pump refrigeration cycle to make a refrigerant. When used as a compressor, in particular, immediately after switching from the heating operation refrigeration cycle to the defrosting operation refrigeration cycle, the discharge chamber pressure becomes a low pressure state and the suction chamber pressure becomes a high pressure state. From the back pressure chamber 120 to the balance passage 1
Backflow through the back pressure chamber 120 and the drive shaft 105.
Together to efflux lubricating oil reservoir to the oil reservoir 9 to the bearing sliding portion, the refrigerant gas flowing back to the oil reservoir 9 diffuses the lubricating oil of the oil reservoir 9, outside of the compressor with the result ejection out refrigerant gas It is caused to flow out to the piping system, and a shortage of lubricating oil in the oil sump 9 occurs temporarily. Therefore, back pressure instability of the back pressure chamber 120, insufficient lubrication oil, and insufficient lubrication oil in the bearing sliding portion occur almost at the same time, and the abnormal noise due to the inclination of the orbiting scroll 114 with respect to the drive shaft main axis and collision with related parts. However, there was a problem of causing abnormal wear.

Further, the structure in which the back pressure chamber 220 and the compression chamber 240 as shown in FIG. 6 only communicate with each other through the balance passage 226 having a fine hole has the same problem as in the case of FIG. That is, immediately after switching from the heating operation refrigeration cycle to the defrosting operation refrigeration cycle, the suction chamber pressure becomes a high pressure state, the compression chamber in the middle of compression raises an abnormal pressure, and the refrigerant gas passes through the balance passage 226 and the back pressure chamber 220 flows. Backflow to the same, causing the same lack of lubricating oil as described above. Immediately after starting the compressor, since the discharge pressure and the back pressure chamber pressure are low, the refrigerant gas during compression flows back into the back pressure chamber 220, and as a result, the pressure in the back pressure chamber 220 is higher than the pressure in the oil sump 209. In this state, there is a problem in that the oil cannot be supplied from the oil sump 209 to the back pressure chamber 220 and the sliding portion is damaged. In addition, the refrigerant gas flows backward into the back pressure chamber 220 even during overload operation due to a so-called liquid compression phenomenon that compresses the refrigerant liquid or a large amount of lubricating oil to raise the abnormal pressure in the compression chamber, and the back pressure chamber to the orbiting scroll 215. Is increased abnormally, so that the orbiting scroll 215 moves from the fixed scroll 223.
There has been a problem that the drive shaft 205 is separated in the main axis direction to expand the compression chamber gap and prevent the compression chamber pressure from dropping rapidly, resulting in significant damage to the compressor.

On the other hand, there are measures to prevent abnormal pressure rise in the back pressure chamber.
Then, it is proposed in JP-A-57-76291.
There is a back pressure control means. That is, the back pressure chamber and the inhalation system are connected.
The valve body and the pressing spring are installed in the path to
Closes the above path via the valve body and opens when abnormally high back pressure
It is a structure to go by. This back pressure control means is shown in FIG.
When applied to scroll gas compressors such as
When the compressor is cold, it is discharged in the initial stage or when the compressor is operating at low speed.
The outlet pressure is low and the oil sump (109, 20
9) The pressure difference in the oil supply passage between the suction system and the compression chamber is small.
When the operating condition is short, the back pressure control means closes the oil supply passage.
Since it is in the cutoff state, the sliding parts related to the oil supply passage are
There was a problem of causing damage.

The present invention solves the above problems.
Control the opening of the throttle passage in the middle of the oil supply passage to control the back pressure chamber pressure.
By adjusting the forces, and to provide a superior efficiency and durability scroll <br/> Lumpur gas compressors.

[0009]

Means for Solving the Problems] Scroll gas compressors of the present invention in order to achieve the above object, Through the discharge port
Back pressure chamber and suction chamber of the orbiting scroll or
Equipped with the fuel supply passage through sequentially into the compression chamber, the oil supply passage to the oil supply <br/> communication path Katsuso having a check valve function of permitting fluid flow of only from the back pressure chamber to the suction chamber or compression chamber The refueling passage control device is provided with a control device, and has an opening adjustment function of narrowing the passage when the temperature of the refueling passage increases and expanding the passage when the temperature of the refueling passage decreases.

[0010]

According to the present invention, the discharge side pressure immediately after the cold start of the compressor or the switching of the high and low pressure side piping system,
Low back pressure chamber pressure and the gas from the suction chamber or compression chamber, such as when the suction side pressure is relatively high with respect to the discharge-side pressure is locked inhibitory flowing back to the back pressure chamber, abnormal pressure in the back pressure chamber The rise is prevented and the back pressure chamber and the lubricating oil stored upstream of the back pressure chamber are prevented from flowing out, so that the lubricating oil is secured. Also, discharge
Increase the compression load by following the expansion of the differential pressure between the suction side and the suction side.
Along with this, the temperature rise of the oil supply passage control device reduces the opening of the passage.
Excessive lubricating oil flow from the oil reservoir to the suction side and compression chamber
Can be prevented to improve durability and compression efficiency.
It

[0011]

DESCRIPTION OF THE PREFERRED EMBODIMENTS A scroll gas compressor according to an embodiment of the present invention will be described below with reference to the drawings. 1 is a vertical sectional view of a scroll refrigerant compressor according to a first embodiment of the present invention, and FIG. 2 is an enlarged sectional view of a portion A in FIG. FIG.
In the figure, 1 is a closed shell, 2 is a body frame press-fitted and fixed to the closed shell 1, 3 and 4 are bearings provided in the center of the body frame 2, and 5 is an oil hole 6 which is supported by the bearings 3 and 4 and penetrates therethrough. And a bearing 4 and a drive shaft that communicates with the oil hole 6 and is provided with an oil hole 7, the upper end of which is provided with an eccentric shaft portion 8 and the lower end of which extends to an oil reservoir 9 at the bottom of the closed shell 1. It is stretched and immersed. Reference numeral 10 denotes a motor, the rotor 11 of which is fixed to the drive shaft 5 and the stator 12 of which is fixed to the closed shell 1 by press fitting. The wrap support disk 15 of the orbiting scroll 14, which is connected to the eccentric shaft portion 8 and has the bearing portion 13 at the center thereof to form the back pressure chamber C20c by the eccentric shaft portion 8 and the bearing portion 13, is the orbiting scroll upright on its upper surface. The wrap 16 is integrally formed, and the lower surface of the wrap 16 is supported by a thrust bearing seat 17 protruding into an upper opening hole of the main body frame 2. The orbiting scroll wrap 16 has a spiral shape in a plan view, and has a rectangular vertical cross section in parallel with the adjacent orbiting scroll wraps 16. The Oldham ring 18 for rotation prevention is
A flat ring is provided with parallel key-shaped key portions that are orthogonal to each other on both sides, and is provided between the lap support disk 15 and the thrust bearing seat 17.

The key portion on the upper surface side of the Oldham ring 18 is a key groove (not shown) provided on the back surface of the lap support disk 15, and the key portion on the lower surface side is a key groove 19 provided on the thrust bearing seat 17. The bearing portion 13 of the wrap support disk 15 makes a circular motion around the axis of the drive shaft 5 by the rotation of the drive shaft 5, and the orbiting scroll wrap 16
Makes a turning motion. Further, the end plate 21 of the fixed scroll 34, which serves as the back pressure chamber 20 of the lap support disk 15 by closing the upper end opening hole in the upper end surface of the main body frame 2, together with the thrust bearing seat 17, the lap support disk of the orbiting scroll 14.
Mounting et been 15 so as to sandwich a minute gap, the turning scroll
The back pressure chamber 20 of the valve 14 is formed. The back pressure chamber 20 is partitioned by the lap support disk 15, and the back pressure on the outer peripheral surface side is divided.
The chamber A 20a is divided into a back pressure chamber B 20b on the back side. The end plate 21 is provided with an annular suction chamber 22 inside thereof. A fixed scroll wrap 2 parallel to the orbiting scroll wrap 16 and having the same shape and size is provided inside the suction chamber 22.
In the central part of the spiral of 3, the discharge space 24
The discharge port 25 is provided. The suction chamber 22 and the back pressure chamber A 22 are opened at the sliding surface with respect to the lap support disk 15.
The end plate 21 is provided with a fine balancing passage 26 communicating with a.
Is provided balancing passage 27 and the gas thrust bearing seat 17 of the small hole for communicating the back pressure chamber A 22a and the back pressure chamber B 22b, the orbiting wrap support disk 15 is in a predetermined angular range (outermost
The balance passage 26 and the balance passage 27 are arranged to communicate with each other only when the suction volume of the compression chamber on the side is in the process of increasing .

As shown in FIG . 2, in the middle of the balance passage 26.
During the case 40 to the mirror plate 21 is configured so as to narrow the openings of both ends of the press-fitted balance passage 26, the steel ball 41 on the upstream side of the center of the passage, the coil spring 42 on the downstream side The refueling passage control device 43 is installed and constitutes the refueling passage control device 43. When the temperature of the coil spring 42 rises, the coil spring 42 expands to urge the steel ball 41 to gradually narrow the balance passage 26.
However, when the temperature of the steel ball 41 is finally closed and the temperature of the steel ball 41 decreases, the steel ball 41 contracts to weaken the urging force on the steel ball 41, and the steel ball 41 acts on the basis of the pressure difference between the back pressure chamber 20 and the suction chamber 22. The steel ball 41 is constantly urged with a shape memory characteristic of moving the steel ball 41 against the back pressure to the ball 41 and expanding the balance passage 26. A suction pipe 28 penetrating the hermetic shell 1 from the side is connected to the annular suction chamber 22, and a discharge pipe 29 opening toward the inner side surface of the hermetic shell 1 is connected to the upper surface of the hermetic shell 1. There is. A groove 30 is provided on the outer surface of the main body frame 2 press-fitted and fixed to the closed shell 1, and the groove 30 communicates the discharge space 24 on the end plate 21 side of the closed shell 1 with the motor 10 side.

The operation of the scroll refrigerant compressor configured as described above will be described below with reference to FIGS. 1 and 2. That is, the rotor 11 is revolving scroll 14 is orbiting motion with the drive shaft 5 to rotate the driven rotation of the motors 10, the refrigerant gas is sucked into the suction chamber 22 through the suction pipe 28, the refrigerant gas swirling It is confined in a compression chamber formed between the scroll wrap 16 and the fixed scroll wrap 23, compressed along with the orbiting movement of the orbiting scroll wrap 16, discharged from the discharge port 25 to the discharge space 24, and contained in the refrigerant gas. Part of the lubricating oil is separated from the refrigerant gas by its own weight and the like, and is collected in the bottom oil sump 9 through the groove 30 between the closed shell 1 and the main body frame 2 and the remaining lubricating oil is discharged together with the discharged refrigerant gas. Discharge pipe 2
It is carried out to the outside refrigerating cycle through 9. On the other hand, the differential pressure oil supply from the high pressure side oil reservoir 9 to the low pressure side suction chamber 22 via the back pressure chamber 20 formed by being separated from the discharge space 24 by the end plate 21 of the fixed scroll 34 and the main body frame 2 is performed. This is done as follows.

[0015] That is, the temperature in the compressor of each part immediately after startup compressor cooling is low, between the back pressure chamber 20 and the suction chamber 22
Although the pressure difference is small, the balance passage 26 of the small hole is in the open state by releasing the bias to the steel ball 41 with the coil spring 42 contracted, and after the compressor is started, the closed shell 1 filled with the discharge refrigerant gas The highly viscous lubricating oil in the oil sump 9 at the bottom of the shaft passes through minute gaps between the oil holes 6 and 7 provided in the drive shaft 5 and the bearings 3 and 4 supporting the drive shaft 5 and the bearing part 13 of the eccentric shaft part 8. By doing so, the pressure is gradually reduced and the intermediate pressure between the suction pressure and the discharge pressure is supplied to the back pressure chamber 20b. Further, the lubricating oil is intermittently supplied to the back pressure chamber A 20a through a balance passage 27 having a fine hole which is opened and closed intermittently by the orbiting motion of the lap support disk 15 of the orbiting scroll 14, and the balance passage 26
It is intermittently fed between the suction chamber 22 through the are compressed again together with the suction refrigerant gas. Also, after the compressor is started, the temperature inside the compressor rises as the pressure in the discharge chamber rises, and the coil spring 4
Temperature of 2 exceeds the set value when the coil spring 42 is extended to urge the steel ball 41, Ru narrowed balance passage 26. Oil sump 9
While the differential pressure between the back pressure chamber 20 and the back pressure chamber 20 increases, the lubricating oil having improved fluidity flows into the suction chamber 22 through the sliding surface between the end plate 21 and the lap support disk 15. Incorporating this scroll refrigerant compressor into the heat pump type refrigeration cycle,
Immediately after switching from the heating operation refrigeration cycle to the defrosting operation refrigeration cycle, the refrigerant gas flows from the suction chamber 22 to the back pressure chamber 20 because the discharge chamber pressure becomes a low pressure state and the suction chamber pressure becomes a high pressure state. The steel balls 41 provided in the balance passage 26 close the passages due to the check valve action, and the refrigerant gas flows back to the oil reservoir 9 via the back pressure chamber 20 . prevent, prevent seizure of the lubricating oil flowing out and the sliding surface of the back pressure chamber 20 and the bearing sliding surface.

According to this differential pressure oil supply system, the pressure of the back pressure chamber 20 on the back surface of the lap support disk 15 can be freely set from the state close to the discharge pressure to the state close to the suction pressure by adjusting the passage resistance of the oil supply passage. Therefore, the load difference between the back-side biasing force acting on the back surface of the lap support disk 15 and the gas pressure load in the compression chamber can be freely adjusted, so that the lap support disk 15 can be pressed against the end plate 21 side. Two
It can also be pushed away from the thrust bearing seat 17 side. In the present embodiment, the lap support disk 15 in the case where the viscosity of the lubricating oil is low, such as during steady operation, is such that the thrust force acts on the end plate 21 side, and the lap in the case where the viscosity of the lubricating oil is high, such as immediately after cold start. The support disk 15 is provided in the back pressure chamber 20 so that the thrust force acts on the thrust bearing seat 17 side.
The area and pressure are set, and the oil supply passage is designed to achieve that pressure.
The passage opening of the control device 43 is set. In the present embodiment, the downstream opening of the balance passage 26 is connected to the end of the coil spring 42. However, as shown in FIG. 3, the coil spring 42a is near the center or the steel ball 41.
The balance passage equipped with the oil supply passage control device 43a near the
A structure communicating with the passage 26a , and further, as shown in FIG.
The supply oil passage control device 43b having a coil spring 42b to
Configuration provided balance passage 27 provided in the thrust bearing seat 17 and may be a combination of these configurations.

[0017] In the above embodiment, although the oil supply passage downstream of the back pressure chamber 20 and the suction chamber, the conventional scroll pressure 6
Like the case of compressor, it may be the oil supply passage downstream of the back pressure chamber 20 into the compression chamber during the compression step may be provided with a similar oil supply passage control device and Figure 2 during the oil supply passage. The oil supply passage control device in this oil supply passage configuration also functions as a check valve described below. That is, immediately after the cold start of the compressor, the pressure of the discharge chamber communicating with the compressor external piping system is low, and the lubricating oil may flow into the back pressure chamber 20 from the oil reservoir 9 due to the differential pressure.
Since the pressure is small, the pressure in the back pressure chamber 20 may be momentarily lower than the fluctuating pressure in the compression chamber communicating with the back pressure chamber 20.
Therefore, the refrigerant gas in the middle of compression tries to flow into the back pressure chamber 20, but the check valve action of the oil supply passage control device 43 prevents the back flow to the back pressure chamber 20. As a result, the back pressure chamber 20 is blocked.
There is no blow-through of the refrigerant gas from the oil supply passage to the oil sump 9.
Prevent lubricating oil spill and the sliding portion seizure associated therewith accompanying. In addition, instantaneous abnormal pressure rise in the compression chamber (liquid compression phenomenon) that occurs due to compression of the refrigerant liquid and a large amount of lubricating oil during compression.
It also prevents the refrigerant gas from flowing back to the back pressure chamber 20. As a result, the abnormal pressure rise in the back pressure chamber 20 and the back pressure biasing force increase to the orbiting scroll 14 are prevented, the orbiting scroll 14 is separated from the fixed scroll 34 in the axial direction, and the pressure in the compression chamber is suddenly reduced. A load reducing action can be performed.

As described above, according to the above embodiment, the discharge port
From the oil sump 9 which acts on the discharge gas pressure through the port 25 ,
The oil holes 6 and 7 provided in the drive shaft 5, the bearings 3 and 4 supporting the drive shaft 5, the minute gaps in the bearing portion 13 of the eccentric shaft portion 8, the back pressure chamber 20 and the suction chamber 22 of the orbiting scroll 14, A back pressure chamber 2 provided with a refueling passage that sequentially passes through the refueling passage.
0 on the end plate 21 between the suction chamber 22 and
The valve body of the steel ball 41 and the upstream of the valve body in the balance passage 26 that has
In the configuration of arranging the supply oil passage controller 43 Do that because the coil spring 42 which urges the side, the coil spring 4
2 expands to the steel ball 41 when its own temperature rises.
Increase the urging force and move the steel ball 41 to the upstream side for balance
If the opening of the passage 26 is narrowed and the temperature of itself decreases,
The balance passage 26 of the balance passage 26 is reduced by reducing the urging force to the steel ball 41.
Equipped with an opening adjustment function that has a shape memory characteristic that widens the opening
As a result, the compressor discharges for a while immediately after the cold start.
The pressure of the lubricating oil flowing from the oil sump 9 into the back pressure chamber 20 is low.
Even if the pressure is low and the viscosity is high, the oil supply passage control device 43
Since the opening of the throttle passage of the balance hole 26 of the
Lubricating oil from the back pressure chamber 20 through the bearing sliding portion to the suction chamber
It becomes easy to be supplied with the differential pressure oil flowing into the
Therefore, lubrication of sliding parts is ensured at the initial stage of compressor startup, improving durability.
You can go up.

During stable operation of the compressor, the oil sump 9 and suction
While the differential pressure between the chamber 22 and the
The temperature also rises due to sliding heat and compression heat,
Lubricating oil has low viscosity and good fluidity, but oil supply passage control device
The opening of the throttle passage of the balance hole 26 of 43 is narrowed.
Therefore, excessive inflow of lubricating oil into the suction chamber 22 is suppressed,
It is possible to prevent an increase in input due to the compression of lubricating oil in the compression chamber.
It

Further , according to the above embodiment, the steel ball 41 and the carp are
The lube spring 42 is located upstream of the balance passage 26 (back pressure chamber 2
0) Allows opening only from the downstream side (suction chamber 22)
By being arranged to have a check valve action, this scroll refrigerant compressor is incorporated into a heat pump type refrigeration cycle, and immediately after switching from the heating operation refrigeration cycle to the defrosting operation refrigeration cycle, the discharge chamber pressure becomes a low pressure state. Since the suction chamber pressure is high , the refrigerant gas is transferred from the suction chamber 22 to the back pressure chamber 20 through the balance passages 26 and 27.
Although trying to flow backward, the steel ball 4 provided in the balance passage 26
Close the passage by the check valve action of 1, refrigerant gas via the back pressure chamber 20 and prevented from flowing back to the oil reservoir 9, the back pressure chamber
It is possible to prevent the lubricating oil from leaking from the sliding surface 20 and the bearing and seizure of the sliding surface . Especially, the defrosting operation from the heating operation refrigeration cycle
Suction chamber 22 and suction chamber immediately after switching to the refrigeration cycle
High pressure refrigerant gas flows into the compression chamber adjacent to 22
As it rises, the coil spring 42 expands and attaches to the steel ball 41.
Increase power. As a result, the check valve action of the steel ball 41
And the durability of the sliding surface can be further improved .

[0021]

As described above , the first aspect of the present invention is to provide a fixed disc.
Oil leading to the discharge port provided at the center of the roll wrap
Reservoir, back pressure chamber of orbiting scroll, fixed scroll wrap
Equipped with the fuel supply passage through the suction chamber or compression chamber provided outside sequentially arranged oil supply passage control device between the oil supply passage way in the back pressure chamber and the suction chamber or compression chamber, the oil supply passage
The control device narrows its passage when its own temperature rises.
To widen its passage when its own temperature drops
With the opening adjustment function that has a shape memory characteristic that operates, the discharge pressure for a while immediately after the cold start of the compressor
Is low, the pressure of the lubricating oil flowing from the oil reservoir into the back pressure chamber is low
And even if the viscosity is high, opening the throttle passage of the oil supply passage control device
Due to its wide range, the lubricating oil in the oil reservoir can be transferred from the back pressure chamber to the suction chamber or
Even if the differential pressure to the compression chamber is small, the differential pressure will eventually reach the compression chamber.
Since it becomes easy to refuel, differential pressure supply at the initial stage of compressor startup
It is possible to secure lubrication of sliding parts with oil and improve durability.
it can. In addition, during stable operation of the compressor,
The pressure difference between the compressor and
The temperature also rises due to sliding heat and compression heat,
Lubricating oil has low viscosity and good fluidity, but oil supply passage control device
Since the opening of the throttle passage is narrowed,
Lubricating in the compression chamber by suppressing excessive inflow of lubricating oil into the compression chamber
Prevents an increase in input due to oil compression and moistens the compression chamber.
A proper amount of lubricating oil can be introduced. As a result, the lubricating oil
A membrane action seals the compression chamber gap to improve compression efficiency.
Can be. That is, the suction chamber according to the compressor load state
Or by providing a function to adjust the differential pressure oil supply to the compression chamber
As a result, it is possible to prevent input increase and improve compression efficiency. In addition, vomiting
During high load operation where the output pressure is high, the temperature rise in each part of the compressor
The oil supply passage located between the back pressure chamber and the suction chamber or compression chamber.
Since the passage opening of the road control device is narrowed, the lubricating oil from the oil reservoir
The back pressure chamber is easily raised to the required pressure by the inflow,
The orbiting scroll can be biased to the fixed scroll with appropriate force.
Can be. Conversely, during low load operation where the discharge pressure is low
The temperature of each part of the compressor drops
Since the opening of the passage between the entrance and compression chambers increases, back pressure
The chamber pressure can be easily lowered and the orbiting scroll can be fixed.
Substantial compression load that can be biased to the side of the roll with appropriate force
The back pressure chamber pressure can be adjusted according to the
Can maintain efficiency.

A second aspect of the present invention is a fuel supply passage control device.
Urges the valve body and the valve body toward the upstream side of the oil supply passage
Spring device, which has its own temperature
When it rises, it increases the urging force on the valve body and the temperature of itself decreases.
When lowered, it has a shape memory characteristic that weakens the biasing force on the valve body,
Valve body and spring device only from upstream side to downstream side of oil supply passage
Is arranged so as to have a check valve action that allows the opening of the
As a result, when the discharge side pressure, the back pressure chamber pressure is low, and the suction side pressure is high, such as immediately after the cold start of the compressor or immediately after switching the high pressure and low pressure side piping systems, the gas is supplied to the oil supply passage.
Via the control unit to prevent the backflow of whether we back pressure chamber the suction chamber or compression chamber, prevents the abnormal pressure rise in the back pressure chamber, reservoir of lubricating oil to the back pressure chamber is oil supply passage upstream oil It can be prevented from flowing into the sump . Further, it is possible to prevent the gas from flowing into the oil reservoir and prevent the lubricating oil from flowing out of the compressor. As a result, it is possible to prevent the durability of the sliding surface related to the back pressure chamber from decreasing. Further, the lubrication oil film interposed on the sliding portion, it is possible to reduce the noise, vibration generated from the sliding portion by the oil film cushioning effects. Further, by preventing the abnormal pressure rise in the back pressure chamber, without excessively pressing the orbiting scroll in the axial direction of the fixed scroll, the axis also orbiting scroll when the compression chamber pressure rises abnormally from the fixed scroll Direction , the compression chamber pressure is reduced to prevent overload operation, and the durability of the compressor can be improved. Especially when the compressor is cold
Immediately after switching the pressure and low pressure side piping system,
The compression chamber adjacent to the suction chamber is heated by the inflow of high-pressure gas.
As it rises, the spring device expands, increasing the biasing force on the valve body.
You. As a result, the check valve action of the valve body is well sealed.
The check valve function of the oil supply passage control device described above
More the utility is intended to achieve the numerous advantages including enhanced.

[Brief description of drawings]

FIG. 1 is a vertical sectional view of a scroll refrigerant compressor according to a first embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view of part A in FIG.

FIG. 3 is a main part of a scroll refrigerant compressor according to the second embodiment.
Partial cross section

FIG. 4 is a main part of a scroll refrigerant compressor according to the third embodiment.
Partial cross section

FIG. 5 is a vertical sectional view of a conventional scroll compressor.

FIG. 6 is a vertical sectional view of the other scroll compressor.

[Explanation of symbols]

 1 Sealed Shell 2 Body Frame 5 Drive Shaft 10 Motor 14 Orbiting Scroll 15 Lap Support Disc 16 Orbiting Scroll Wrap 20 Back Pressure Chamber 21 End Plate 22 Suction Chamber 23 Fixed Scroll Lap 25 Discharge Port 26, 26a, 27 Balance Passage 34 Fixed Scroll 41 Steel Ball 42, 42a, 42b Coil spring 43, 43a, 43b Oil supply passage control device

Continuation of front page (51) Int.Cl. ⁶ Identification number Office reference number FI technical display area F04C 29/06 D

Claims (2)

[Claims] Was 1. A engage the orbiting scroll wrap on the lap support disk forming part of the orbiting scroll relative to the spiral of the fixed scroll wrap formed on one surface of the end plate forming part of the fixed scroll freely oscillating , Both the skull
A spiral wound compression space is formed between the
A discharge port is provided in the center of the roll wrap, and a suction chamber is formed outside the fixed scroll wrap, and the wrap support disk is arranged in a loose state between the main body frame supporting the drive shaft and the end plate. And the orbiting scroll
Next to the back pressure chamber for urging the
In contact with each other, the orbiting scroll is engaged with the rotation preventing mechanism to compress the fluid by utilizing the volume change of the compression chamber formed between the fixed scroll wrap and the orbiting scroll wrap. the scroll type compression mechanism is formed, the
Oil reservoir communicating with the discharge port, the back pressure chamber, lubrication between the suction chamber or with the oil supply passage passing through the compression chamber successively, wherein said back pressure chamber of the oil supply passage middle suction chamber or the compression chamber A passage control device is installed and the lubrication passage control device is installed.
When the temperature of its own rises, it narrows its passage,
When the temperature of itself decreases, it operates to widen the passage.
A scroll gas compressor having an opening adjustment function having shape memory characteristics . 2. The oil supply passage control device includes a valve body and the valve body.
Do not use a spring device that biases the oil supply passage toward the upstream side.
When the temperature of the spring device rises,
When the urging force on the body increases and the temperature of itself decreases,
The valve body has a shape memory characteristic that weakens the biasing force to the valve body.
And the spring device from the upstream side to the downstream side of the oil supply passage.
Arranged to have a check valve action that allows the opening of the chisel
The scroll gas compressor according to claim 1, further comprising: