JP2674562B2 - Scroll refrigerant compressor with refueling control means - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll refrigerant compressor, and relates to a back pressure chamber of an orbiting scroll and a back of a thrust bearing.
It relates to the supply of lubricating oil to the surface portion . 2. Description of the Related Art A scroll compressor having low vibration and low noise characteristics has a suction chamber at the outer periphery of a spiral compression space, and a discharge port provided at the center of the spiral to prevent the flow of compressed fluid. A single direction of flow does not require a discharge valve such as a reciprocating compressor or a rotary compressor to compress the fluid, the compression ratio is constant, the discharge pulsation is relatively small, and a large discharge space is not required. Is generally known. Further, in order to further improve the axial sealing of the compression chamber and the vibration and noise characteristics, as a measure for reducing the instantaneous pressure change of the compression chamber and the jumping phenomenon of the orbiting scroll during high-speed operation of the compressor, FIG. Eight configurations are considered. In the figure, the end plate 1001a of the orbiting scroll 1001 connected to the drive pin 1007a at the tip of the drive shaft 1007 is the end plate 100 of the fixed scroll 1002.
2a and the frame 1008 are supported by a small gap,
It prevents the orbiting scroll 1001a from separating or jumping from the fixed scroll 1002 when the compression chamber pressure changes instantaneously or the inertial force of the rotating member changes, such as when the compressor is started, stopped, or operated at high speed. Scroll 1
A small gap in the axial direction between 001 and the fixed scroll 1002 is secured to seal the compression chamber to improve the compression efficiency, and at the same time, a device for preventing abnormal noise, vibration, and durability deterioration of the sliding portion caused by the collision between the members. Has been done. [0004] Also, in order to further ensure axial sealing of the compression chamber, (1) by introducing into the housing chamber H gas from its discharge line in vacuo, the fixed scroll and the orbiting scroll 1001 (2) A gas in the closed space is introduced into the housing chamber H through a small hole 1011 provided in the end plate 1001a of the orbiting scroll 1001, and the orbiting scroll 1001 is caused by the gas pressure. The fixed scroll 1002 is biased to hermetically seal the closed space 1006 (Japanese Patent Laid-Open No. 55-142902, US Pat. No. 3,994,633, etc.). [0005] Also, sealing of the compression chamber, the durability of the sliding portion, the form of the specific scroll refrigerant compressor noise and vibration and more improvement has been proposed in Japanese Patent Publication No. Sho 62-37238. That is, in FIG. 3 of the publication, the discharge gas pressure acts on the lubricating oil 14 accumulated at the bottom of the closed container 6. After this lubricating oil 14 has flowed through the eccentric hole 13 of the shaft 4 into the back pressure chamber 9a of the orbiting scroll member 2 under reduced pressure,
A differential pressure oil supply passage that flows into the compression chamber 5b through a small hole 2d provided in the orbiting scroll member 2 is shown. The orbiting scroll member 2 is configured to be pressed against the fixed scroll member 1 by the lubricating oil pressure in the back pressure chamber 9a. The lubricating oil 14 is supplied to the bearings that support the shaft 4 and the sliding surfaces of the orbiting scroll member 2 in the course of the passage. Further, the lubricating oil that has flowed into the compression chamber 5b seals the gap in the compression chamber 5b with the oil film. Further, when the pressure in the closed container 6 is not so high and differential pressure oil supply to the back pressure chamber 9a does not occur, the gas during compression is compressed through the small hole 1d of the orbiting scroll member 2 in the compression chamber. It is configured to flow into the back pressure chamber 9a from 5b and press the orbiting scroll member 2 against the fixed scroll member 1 to seal the compression chamber 5. However, when this type of structure is used as a refrigerant compressor for air conditioning, it is necessary to compress a fluid such as a reciprocating compressor or a rotary compressor. Due to the configuration that does not require a discharge valve, when the pressure inside the compression chamber rises abnormally due to liquid compression, etc., the gap between the compression chambers is widened to leak the compressed fluid, and the pressure in the compression chamber cannot be lowered. The pressure in the back pressure chamber 9a also becomes high, and the orbiting scroll member 2 is excessively pressed against the fixed scroll member 1 to increase the compression load, damage the parts, and lower the durability of the sliding portion. [0007] Also, since the compressor starts initial relatively high suction pressure, the pressure in the back pressure chamber 9a is also increased, since the excess press the orbiting scroll member 2 to the fixed scroll member 1,
There is a problem that the initial input for starting becomes excessive and the liquid refrigerant stored in the lower layer of the lubricating oil 14 is differentially supplied to each sliding portion before the lubricating oil 14 to cause seizure of the sliding portion. . On the other hand, a measure for solving this kind of problem is a practical method.
It is proposed in the 2-116187 gazette. That is,
In the publication, a movable scroll (orbiting scroll) 9
Discharge pressure action chamber (back pressure chamber) 13 provided on the side opposite to the compression chamber
Selectable between chamber 6 and suction chamber 5 via switching valve 28.
It is installed so that it can communicate with each other at the time of startup or liquid compression.
Communication between suction chamber 5 and pressure action chamber (back pressure chamber) 13
The pressure chamber (back pressure chamber) 13 and the compression chamber
A pressure difference is generated between 10 and it is possible to move by this pressure difference.
Set the scroll (orbiting scroll) 9 to the pressure chamber (back pressure
(Chamber) 13 side to move backward to reduce the compression load
It is. However, in the above configuration, the operation mode
Automatically switches according to the compression load condition (such as at startup)
Because there is no function to operate the valve 28, the compression load
The time for reduction is lost and the load cannot be reduced effectively. Also,
Higher cost due to control function parts of switching valve 28
There was a problem such as becoming. In order to solve the above-mentioned problems, the scroll compressor of the present invention is arranged such that the lubricating oil in the discharge chamber oil reservoir communicating with the discharge port is provided on the back surface of the thrust bearing for supporting the orbiting scroll. Supply to the back pressure chamber of the orbiting scroll
In the structure with the oil supply passage, the thrust bearing
In addition to providing a means to prevent excessive pressing of the crawl, the discharge chamber
When the pressure in the oil reservoir is below the pressure in the compression chamber,
The biased valve body closes the oil supply passage, and the pressure in the discharge chamber oil reservoir
Pressure exceeds the pressure in the compression chamber, the differential pressure causes the valve element to
Install the oil supply passage control valve device equipped with the valve body that opens the oil passage.
It is provided upstream of the back surface of the last bearing and the back pressure chamber . According to the present invention, since the thrust bearing and the back pressure chamber are not supplied with liquid refrigerant or oil is supplied to the orbiting scroll at the initial stage of the compressor , the orbiting scroll is not pressed toward the fixed scroll. Since the compression chamber gap is generated, the compression load does not increase rapidly and the compression load gradually increases. With the passage of time after starting the compressor, the operating pressure of the oil reservoir exceeds the pressure of the compression chamber , the liquid refrigerant in the oil reservoir of the discharge chamber evaporates, and only the lubricating oil is supplied to the thrust bearing and the back pressure chamber. Is urged toward the fixed scroll by an appropriate force to seal the compression chamber gap and improve the compression efficiency. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A scroll refrigerant compressor according to an embodiment of the present invention will be described below with reference to the drawings. 1 and 2
In, 101a and 101b are iron closed cases, 1
Reference numeral 80 denotes a mild steel partition plate to which an iron main body frame 105 is fixed by bolts.
It is welded and sealed together with 101b by a single weld bead 181 to partition the insides of the sealed cases 101a and 101b into an upper discharge chamber 102 and a lower drive chamber 106 (low pressure side). The eccentric hole 13 at the upper end of the drive shaft 104 which is supported by the main body frame 105 and is rotationally driven by the motor 103 whose operation is controlled by an inverter power supply (not shown).
The orbiting shaft 118b of the orbiting scroll 118 is fitted into the shaft 6, and the Oldham ring 124 for preventing rotation of the orbiting scroll 118 is constrained by a split pin type parallel pin (not shown) fixed to the main body frame 105. Thrust bearing 120 and orbiting scroll 11 that can move only in the axial direction
A fixed scroll 115 that engages with each groove of 8 and meshes with the orbiting scroll 118 is bolted to a partition plate 180, a discharge port 116 is provided on the end plate 115b of the fixed scroll 115, and a lead is provided on the top surface of the end plate 115b. A valve type oil supply passage control valve device 182 is attached. [0013] scan thrust bearing 120, the seal ring 170 disposed on the back outer part is urged towards the constantly orbiting scroll 118 by the elastic force of the orbiting scroll 118 in contact with the side planar portion of the partition plate 180 The axial movement to the side is restricted. However, the plate thickness of the partition plate 180 is such that the elastic force of the seal ring 170 via the thrust bearing 120 does not press the orbiting scroll 118 against the fixed scroll 115 and hinder the smooth orbiting motion of the orbiting scroll 118. An orbiting scroll 118 sandwiched between a fixed scroll 115 and a thrust bearing 120.
The dimension setting is such that a small axial gap (about 0.020 mm) is secured. The bottom of the discharge chamber 102 serves as a discharge chamber oil sump 134, and an umbrella-shaped punching metal 133 having a large number of small holes is attached to the sealed case 101a at the upper part thereof, and the sealed case 101a and the punching metal 133 are attached.
A filter 183 made of a fine resin wire is packed between and. The discharge chamber 102 communicates with the drive chamber 106 on the low pressure side through a discharge pipe 131 provided on the upper surface of the closed case 101a and an intake pipe 147 provided on the side surface of the closed case 101b via an external refrigeration cycle piping system. There is. A motor chamber oil sump 184 is provided at the bottom of the drive chamber 106. [0014] During the second compression chamber 151 to discharge failure outlet chamber 102 in a normally closed space which does not communicate to the suction chamber 117 and discharge chamber oil reservoir 134, suction oil provided in an opening in the bottom of the end plate 115b A hole 185, a valve space 188 formed between the valve retainer 187 of the oil supply passage control valve device 182 attached to the end plate 115b together with a thin steel plate reed valve 186, and a punch hole 189 of the reed valve 186,
It communicates with a first oil supply passage having a throttle passage formed of an injection hole 152 of an ultrafine passage provided in the end plate 115b. Wrap support disk 118b for supporting the orbiting scroll wrap 118a of the orbiting scroll 118.
The back pressure chamber 139 formed by the thrust bearing 120 and the drive shaft 104 branches off from the middle of the first oil supply passage to form the valve space 188, the punched hole 189a of the reed valve 186, and the end plate 1.
15b is an oil hole A138a, a partition plate 180 is an oil hole B138b of an ultrafine passage, a body frame 1
Oil hole C138c provided in 05, thrust bearing 120
Between the main frame 105 and the main body frame 105, the outer peripheral portion of which is supported and sealed by a rubber seal ring 170. A release gap 127 sealed and an oil hole D138d provided in the thrust bearing 120 Discharge chamber oil sump 1
34. Back pressure chamber 139 and low pressure side drive chamber 1
Between the main frame 105 and the main frame 105 so as to support the bearing gap of the main bearing 112 of the main frame 105, the gap of the eccentric bearing 114, the eccentric oil hole 190 provided in the drive shaft 104, the lateral oil hole 191, and the drive shaft 104. A first lubricating passage having a throttle passage formed by a bearing oil reservoir 193 between a lower bearing 192 provided at the lower end of the main bearing 112 and a main bearing 112, and a bearing gap of the lower bearing 192. Also, the back pressure chamber 139
Between the suction chamber 117 and the suction chamber 117, the sliding surface between the thrust bearing 120 and the lap support disk 118b, and the Oldham ring 124.
Are communicated with each other by a second lubrication passage configured through the sliding surface of the. In FIG. 5, the horizontal axis represents the rotation angle of the drive shaft 104, the vertical axis represents the refrigerant pressure in the compression chamber, and shows the pressure change state of the refrigerant gas during the suction, compression, and discharge processes. Solid line 6
2 shows the pressure change during normal pressure operation, and the dotted line 63 shows the pressure change during abnormal pressure increase operation. In FIG . 6, the horizontal axis represents the rotation angle of the drive shaft 104, the vertical axis represents the refrigerant pressure in the compression chamber, and the solid line 6
4 is an injection hole 152 of the second compression chamber, which is a normally closed space that does not communicate with the discharge chamber 102 or the suction chamber 117.
Of the first compression chambers 161a and 161 which intermittently communicate with the suction chamber 117.
The pressure change at the fixed point of b is shown, and the alternate long and short dash line 66 indicates the third compression chambers 160a, 16a intermittently communicating with the discharge chamber 102.
The pressure change at the fixed point of 0b is shown, and the two-dot chain line 67 indicates the first compression chambers 161a, 161b and the second compression chambers 151a, 1a.
51b shows the pressure change at a fixed point of the compression chamber between 51b and
The double dotted line 68 shows the pressure change in the back pressure chamber 139. [0016] The constructed scroll refrigerant compressor as the following, the operation thereof will be described. [0017] When the drive shaft 104 by motors 103 start driving rotation, the orbiting scroll 118 is a pivoting movement, flows into the driving chamber 106 suction refrigerant gas through the suction pipe 147 from the refrigeration cycle piping system connected to the compressor Then, after part of the lubricating oil contained therein is separated, it is sucked into the suction chamber 117 through the suction passage. The sucked refrigerant gas is trapped in the compression chamber through the first compression chamber which is formed between the orbiting scroll 118 and the fixed scroll 115 and intermittently communicates with the suction chamber 117.
Along with the swirling motion of 18, the second compression chamber, which is always a closed space, and the third compression chamber, which communicates intermittently with the discharge port, are sequentially transferred and compressed, and the discharge chamber 1 passes through the discharge port 116 in the central portion.
It is discharged to 02. The ejection part of the lubricating oil contained in the output refrigerant gas, its own weight and punching discharged refrigerant gas is like attached like on the surface when passing through a filter 183 made of a small hole or fine resin wire metal 133 From the discharge chamber oil reservoir 134, and flows down along the inner wall of the closed case 101a.
Will be collected. The remaining lubricating oil is carried out to the external refrigeration cycle piping system together with the discharge refrigerant gas through the discharge pipe 131, and returns to the compressor through the suction pipe 147 together with the suction refrigerant gas. For a while after the cold start of the compressor, the pressure of the discharge chamber 102 is lower than the pressure of the second compression chamber, so that the lubricating oil in the discharge chamber oil sump 134 is not differentially supplied through the first oil supply passage. By the action of the check valve, the refrigerant gas in the middle of compression does not flow back into the discharge chamber oil sump 134 from the second compression chamber, and does not flow into the release gap 127 of the thrust bearing 120 or the back pressure chamber 139 of the orbiting scroll 118. Each sliding surface is lubricated by the residual lubricating oil of each sliding portion. [0019] In addition, the back pressure chamber 139 and the release gap 127
Since the pressure in the thrust bearing 1 is low due to the pressure of the refrigerant gas in the compression chamber acting on the orbiting scroll 118 in the initial stage of startup,
20 retreats slightly and widens the axial gap in the compression chamber to sharply reduce the pressure in the compression chamber, reducing the initial load on startup. Some time after the cold start of the compressor, after the pressure in the discharge chamber 102 rises above the pressure in the second compression chamber, the lubricating oil in the discharge chamber oil sump 134 is fed to the reed valve 186 of the oil supply passage control valve device 182. Passes through the first oil supply passage against the biasing force. Then, the pressure is gradually reduced, differential pressure oil is supplied to the second compression chamber, and the oil hole 1 of the second oil supply passage formed by branching from the middle of the first oil supply passage.
The pressure is gradually reduced through 38a, 138b, 138c, adjusted to an intermediate pressure between the discharge side pressure and the suction side pressure, and differential pressure oil is supplied to the release gap 127 and the back pressure chamber 139. The lubricating oil differentially supplied to the second compression chamber merges with the lubricating oil that has flowed into the compression chamber together with the suction gas, and seals a minute gap between the adjacent compression chambers with an oil film to prevent compressed refrigerant gas leakage and compression. Discharge chamber 1 with compressed refrigerant gas while lubricating the sliding surfaces between the chambers
It is discharged again to 02. The lubricating oil of intermediate pressure oil is supplied to the LES lease gap 127 and the back pressure chamber 139, it provides a biasing force of the back pressure to the orbiting scroll 118, turning to be cane away from the fixed scroll 115 on the basis of the compression chamber pressure Scroll 1
The downward thrust force acting on 18 is reduced, the thrust load acting on the sliding surface between the orbiting scroll 118 and the thrust bearing 120 is reduced, and the thrust bearing 120 is urged to contact the partition plate 180. Then, the orbiting scroll 118 is sandwiched between the fixed scroll 115 and the thrust bearing 120 with a minute gap, so that the orbiting scroll 118 can smoothly orbit. Further, since the back pressure of the back pressure chamber 139 is adjusted so that the orbiting scroll 118 does not separate from the thrust bearing 120, the orbiting scroll 118 and the thrust bearing 120 are always in sliding contact with each other, and this sliding contact portion is the boundary. The back pressure chamber 139 and the suction chamber 117 are hermetically sealed so that the sliding contact surfaces thereof can be appropriately lubricated to allow leakage of lubricating oil. [0021] When designing equipment, lubricating oil supplied to the back pressure chamber 139 is reduced in pressure when passing through the sliding surface, and mixed with lubricating to suction refrigerant gas sliding surface of the Oldham ring 124 , Flows into the compression chamber again. The remaining lubricating oil is
Through the first lubrication passage, the gap between the swivel shaft 118b and the eccentric hole 136, the eccentric hole 136, the eccentric oil hole 190, and the lateral oil hole 191.
Through the oil supply passage passing through and the gap between the main bearings 112, and then flows into the bearing oil sump 193, and finally reduced in pressure through a minute gap in the lower bearing 192. Then, it flows into the drive chamber 106, a part of it is mixed with the suction refrigerant gas and flows into the compression chamber again, but the remaining lubricating oil is collected in the motor chamber oil sump 184. The lubricating oil of the motors chamber oil reservoir 134 is cooled by natural heat dissipation via the sealed casing 101b, when the oil level becomes high to some extent, the drive chamber 106 is diffused to the lower end of the rotor of the motor 103 Mixed with the refrigerant gas in the inside,
It flows into the compression chamber again and is finally collected in the discharge chamber oil sump 134. Further, in the case where an abnormal pressure rise occurs in the second compression chamber, which is always a closed space, due to the instantaneous liquid compression occurring at the initial stage of cold start or at the time of steady operation, the check refrigerant of the reed valve 186 discharges the compressed refrigerant gas. The thrust bearing 120 does not flow back into the chamber oil sump 134, does not flow into the release gap 127 or the back pressure chamber 139, and does not increase back pressure.
To prevent a continuous abnormal pressure rise. [0023] After compressors stop the suction chamber 117 driving chamber 10
A check valve (not shown) provided in the suction passage between the discharge chamber 102 and the suction chamber 117
Up to the pressure of the discharge chamber 102 through the gap of the compression space, and the reed valve 186 closes the opening end of the oil suction hole 185. [0024] As a result, immediately after the compressor stop the discharge chamber oil reservoir 1
The lubricating oil of 34 is not differentially supplied to the second compression chamber and the back pressure chamber 139, and the lubricating oil of the back pressure chamber 139 is supplied to the drive chamber 106 through the first oil supply passage until the differential pressure becomes less than a certain value. It is returned little by little. [0025] The tail, in the above-described embodiment, the release gap 12
7, the lubricating oil in the discharge chamber oil reservoir 134 was reduced to an intermediate pressure to the back pressure chamber 139 and the thrust bearing 120 and the back pressure chamber 13.
The pressure need not be reduced due to the dimensional configuration of FIG. Further, in the above embodiment, the lubricating oil in the oil reservoir 134 of the discharge chamber is injected into the second compression chamber. However, the oil is injected into the first compression chamber communicating with the suction chamber 117 depending on operating conditions such as compressor operating speed and pressure. Good. As described above, according to the above-described embodiment, the discharge chamber oil sump 13
Since the downstream side of the passage that guides the lubricating oil of No. 4 to the release gap 127 communicates with the back pressure chamber 139 of the orbiting scroll 118, the pressure in the back pressure chamber 139 at the initial stage of compressor startup is low.
The orbiting scroll 118 easily separates from the fixed scroll 115 in the axial direction, which can release the sealing of the compression chamber and contribute to reduction of the input in the initial stage of start-up, and at the time of stable operation of the compressor in which the compression chamber needs to be sealed, the orbiting scroll 118 is Energize the back of the with the lubricating oil of the intermediate pressure between the discharge pressure and the suction pressure,
The thrust force from the orbiting scroll 118 acting on the thrust bearing 120 can be reduced to reduce the input. As a result,
It is possible to reduce the input in the entire operation area from the initial stage of compressor startup to stable operation. Further, although the refrigerant compressor has been described in the above embodiments, similar effects can be expected with other gas compressors such as oxygen, nitrogen, and helium that use lubricating oil. As described above, according to the present invention, the lubricating oil in the oil reservoir of the discharge chamber communicating with the discharge port is the back pressure chamber and the thrust bearing.
Is installed on the side opposite to the compression chamber of the thrust bearing to bias the back pressure.
Supply the suction chamber through at least one of the lease gaps.
In the structure in which the oil supply passage having the throttle passage to be supplied is provided, the orbiting scroll includes the fixed scroll and the thrust bearing.
Between them, there is at least an axial minute gap where an oil film can be formed.
The axial movement position of the thrust bearing so that
Is provided, and the pressure in the discharge chamber oil reservoir is
A valve element that is urged by the pressure difference when the pressure is below the pressure in the compression chamber.
Closes the oil supply passage, and the pressure in the discharge chamber oil reservoir
When the pressure is exceeded, the valve body opens the oil supply passage due to the pressure difference.
Install the oil supply passage control valve device with the valve body that
Since it is installed on the upstream side of the lease gap,
Since it can be opened and closed automatically, it is possible to
Liquid compression etc. occurs in the room and the compression chamber pressure is the discharge chamber oil reservoir pressure.
At the time of the above, the back of the thrust bearing and back pressure are
Supply pressure is reduced by stopping the supply of liquid refrigerant and lubricating oil to the chamber
Therefore, the force acting on the side opposite to the compression chamber of the orbiting scroll is fixed.
The biasing force to the side of the constant scroll is reduced,
The axial pressure from the fixed scroll due to the compression chamber pressure.
When separated, a compression chamber gap is created. As a result, the compression load
Reduce at the right time to effectively reduce input and break the compressor
You can prevent loss. In addition, the orbiting scroll is a thrust bearing.
Since it is not always over-pressed by
The friction loss between the roll and the thrust bearing can be reduced.
You. The orbiting scroll is supported by thrust bearings.
However, the back pressure from the thrust bearing cannot be received.
Therefore, excessive axes of orbiting scroll and fixed scroll
Friction loss can be reduced by avoiding directional contact. Further, the present invention compresses the lubricating oil in the discharge chamber oil reservoir.
The first oil supply passage for supplying the differential pressure to the chamber is provided, and the oil supply passage control valve
The valve body of the device should open and close the first oil supply passage and the oil supply passage synchronously.
The simple structure of the opening and closing means for the first oil supply passage
Can be realized. Further, the pressure in the compression chamber at the initial stage of compressor startup is
When the pressure is higher than the oil sump pressure, the refrigerant flows from the compression chamber to the discharge chamber oil sump.
Of lubricating oil from the compressor
be able to. As a result, the discharge after the compressor is started
Anti compression chamber side and the suction chamber of the orbiting scroll the lubricating oil chamber oil reservoir
The appropriate amount and pressure of oil is applied to the
There is an effect such as being able to improve.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a vertical cross-sectional view of a scroll refrigerant compressor according to an embodiment of the present invention. FIG. 2 is an external view of a reed valve installation of an oil supply passage control valve device in the compressor. Illustration of movement of the compression chamber near the discharge port of the compressor [Fig. 4] Illustration of movement of the compression chamber near the discharge port of the compressor [Fig. 5] Refrigerant gas from the intake stroke to the discharge stroke of the compressor FIG. 6 is a characteristic diagram showing the pressure change at a fixed point in each compression chamber. FIG. 7 is a vertical sectional view of a conventional scroll compressor. FIG. 8 is a partially enlarged view of FIG. 102 discharge chamber 103 motor 104 drive shaft 105 main body frame 115 fixed scroll 115a fixed scroll wrap 115b end plate 116 discharge port 117 suction chamber 118 orbiting scroll 118a orbiting Crawl wrap 118c Wrap support disk 120 Thrust bearing 127 Release gap 134 Discharge chamber oil reservoir 139 Back pressure chamber 182 Oil supply passage control valve device

Claims (1)

(57) [Claims] A scroll-type fixed scroll wrap formed on one surface of an end plate that forms a part of a fixed scroll, and an orbiting scroll wrap on a wrap support disk that forms a part of an orbiting scroll are oscillated and rotatably engaged to form both scrolls. A spiral compression space is formed therebetween, a discharge port is provided at the center of the fixed scroll wrap, a suction chamber is provided outside the fixed scroll wrap, and the compression space extends from the suction side toward the discharge side. Driven by forming a scroll compression mechanism that divides the fluid into multiple compression chambers that move continuously
Attached to the body frame that supports the shaft,
Supports the anti-compression chamber side of the crawl and allows axial movement
The swivel between the thrust bearing and the fixed scroll
The scroll is arranged and the orbiting scroll is
Serial adjacent to the back pressure chamber provided in the anti-compression chamber side, and the lubricating oil is the back pressure chamber of the discharge chamber oil reservoir communicating with the discharge port, wherein
In order to urge the thrust bearing with back pressure, the thrust bearing counter pressure
At least one of the release gaps provided on the shrink chamber side
Therefore, in the configuration in which the oil supply passage including the throttle passage that is supplied to the suction chamber is provided, the orbiting scroll is
At least oil between the constant scroll and the thrust bearing
To be arranged with a small axial gap that allows film formation,
A means for restricting the axial movement position of the thrust bearing is provided.
At the same time, the pressure in the discharge chamber oil reservoir is equal to the pressure in the compression chamber.
The valve element urged by the pressure difference is
The passage is closed and the pressure in the discharge chamber oil reservoir is equal to the pressure in the compression chamber.
When the force is exceeded, the pressure difference causes the valve body to
An oil supply passage control valve device including the valve body for opening a passage,
A scroll refrigerant compressor provided upstream of the back pressure chamber and the release gap . 2. The first supply that supplies the differential pressure of the lubricating oil in the discharge chamber oil reservoir to the compression chamber
An oil passage is provided, and the valve body of the oil supply passage control valve device is provided with the first supply valve.
The scroll refrigerant compressor according to claim 1, wherein the oil passage and the oil supply passage are configured to be opened and closed at the same time .