JP2002130159A - Helium scroll compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a helium compressor for reducing the size and weight, internally storing a protective device means of an electric motor in the compressor, and having high reliability. SOLUTION: This helium scroll compressor is characterized by setting the suction piping size and the delivery piping size to the ratio indicated in the following expression by using helium gas as operating gas. Zs=0.0040 to 0.0046, and Zd=0.0035 to 0.0039. Here, Zs: the suction piping size Bs (an inch) and the stroke volume of the compressor, and Zd: the delivery piping size Bd (an inch) and the stroke volume of the compressor.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a hermetic scroll compressor used for a helium compressor for a cryopump device in an ultra-high vacuum field using helium gas as a working gas.

[0002]

2. Description of the Related Art In a conventional hermetic scroll compressor for helium, as a high-pressure chamber type scroll compressor in which the hermetic container is maintained at a high pressure state, for example, there is one disclosed in Japanese Patent Application Laid-Open No. 4-301191.

[0003]

There has been no scroll compressor for large-scale helium with a rated output of 7.5 kW or 9 kW and a high-efficiency helium compressor. I didn't have the ability. Further, in the above-mentioned conventional art, in the hermetic scroll compressor for helium, the size of the suction pipe and the discharge pipe is the same as that of the compressor for air conditioning, so that the pipe size becomes too large for helium. Therefore, there is a problem inherent to the helium compressor that the bending radius of the pipe becomes large and the overall size of the helium compressor and the helium compressor unit become too large.

[0004] Further, since the gas circulation amount is very small as compared with air conditioning applications and the motor cooling effect of helium gas itself is small, in the case of a horizontal scroll compressor for helium,
There is a problem inherent to the helium compressor that the cooling oil becomes difficult to reach the upper motor, and as a result, the coil temperature becomes abnormally high and the motor burns out.

The present invention solves the above-mentioned problems and reduces the size,
It is an object of the present invention to provide a highly reliable helium compressor in which a helium compressor and a compressor unit with reduced weight are realized, and a protection device for the motor is incorporated in the compressor for protection of the motor. .

[0006]

A solution for the order to achieve this object, the present invention provides a helium scroll compressor using helium gas as a working gas, swept volume of the compressor a 160cm ³ ~180cm ^3, A scroll compressor comprising: a fixed scroll and an orbiting scroll meshing with each other, having a scroll tooth profile with a set volume ratio Vr of a scroll wrap portion of 1.8 to 2.1 shown in the following equation.

[0007]

(Equation 2)

A scroll compressor for helium using helium gas as a working gas, wherein the size of the suction pipe and the size of the discharge pipe are the same and the size of the pipe is set in the range of the ratio shown in the following equation. Structure.

[0009]

Zs = 0.0027 to 0.0046 (Equation 3)

[0010]

Where Zs: ratio of suction pipe size Bs (inch) to compressor stroke volume Vth (cm ³ / rev) (= Bs / Vth) Zd: discharge pipe The ratio between the size Bd (inch) and the stroke volume Vth (cm ³ / rev) of the compressor (= Bd / Vth) Further, the fixed scroll is formed by penetrating an oil injection pipe for cooling the working helium gas into the closed vessel. In a helium scroll compressor equipped with an oil injection mechanism connected to an oil injection port provided on an end plate portion of the helium and having an oil outlet piping portion for guiding injection oil out of the machine from a lower portion of the container, a suction piping size and a discharge piping A scroll compressor structure for helium, characterized in that the size and the size of the oil injection pipe and the oil outlet pipe are all the same.

In particular, when the suction pipe size, the discharge pipe size, and the pipe size of the oil injection pipe and the oil outlet pipe are all the same, the pipe size is set in the range of the ratio shown in the following equation. It is.

[0012]

Zs = 0.0027 to 0.0046 (Equation 5)

[0013]

Zd = Zs = Zo (Equation 6) where Zs is a ratio (= Bs / Vt) between the suction pipe size Bs (inch) and the stroke volume Vth (cm ³ / rev) of the compressor.
h) Zd: ratio of discharge pipe size Bd (inch) to compressor stroke volume Vth (cm ³ / rev) (= Bd / Vth) Zo: size Bo (inch) of oil injection pipe or oil outlet pipe and compression Machine stroke volume Vth (cm ³ / re
v) (= Bo / Vth) Further, a scroll compressor unit and an electric motor unit are housed in a closed container, and the scroll compressor unit is a fixed scroll in which a spiral wrap is erected on a disk-shaped end plate. The orbiting scroll and the orbiting scroll are engaged with each other with the wrap inside, and the orbiting scroll is engaged with an eccentric mechanism connected to the rotating shaft, and makes the orbiting scroll orbit relative to the fixed scroll without rotating, thereby cooling the working helium gas. An oil injection mechanism for penetrating an oil injection pipe through the sealed container for connection to an oil injection port provided on the end plate portion of the fixed scroll, and a gas discharge chamber from the side end of the closed container toward the opposite side. And a motor chamber are defined by a frame, and an oil reservoir is provided below both chambers. The fixed scroll has a discharge port opened at the center and an upper peripheral part. An open suction port is provided, gas is sucked from the suction port, the volume is reduced around the compression chamber formed by both scrolls to compress the gas, and the compressed gas is discharged from the discharge port into the discharge chamber. Further, the gas reaches the motor chamber via the gas passage at the upper part, and then discharges gas to the outside via a discharge pipe, and the axis of the crankshaft driven by the motor for driving the orbiting scroll is moved in the horizontal direction. The working gas is helium gas in the horizontal hermetic scroll compressor installed in the air conditioner, and a thermal sensor is embedded in the upper half of the coil end on the anti-scroll compressor side of the electric motor to detect an abnormal temperature of the coil temperature. A horizontal hermetic helium scroll compressor structure incorporating a motor protection device as described above.

[0014]

DESCRIPTION OF THE PREFERRED EMBODIMENTS One embodiment of the present invention will be described below in detail with reference to FIGS. FIG. 1 is a longitudinal sectional view showing one embodiment of an oil-filled hermetic scroll compressor of the present invention in a horizontal structure of the present invention. The pipe connection shows an example of a brazing method. As shown in FIG. 1, the working gas is helium gas, and an oil injection pipe 31 for cooling the working helium gas is connected to the S cap 1 of the closed vessel 1.
a of the fixed scroll 5 is connected to an oil injection port 22 provided in the end plate portion 5a of the fixed scroll 5, and the opening of the oil injection port 22 is opened facing the tooth tip surface of the wrap 6b of the orbiting scroll 6. are doing. The scroll compressor section 250 is provided on the suction pipe 17a side in the closed vessel 1, and the electric motor section 3 is provided on the opposite side.
Is stored. The inside of the sealed container 1 is a discharge chamber 2a.
And a motor room 2d with the frame 11 interposed therebetween.

The scroll compressor section 250 forms a compression chamber (closed space) 8 by interlocking the fixed scroll 5 and the orbiting scroll 6 with each other. An oil injection pipe 31 for cooling the working helium gas penetrates through the side end 1a of the closed vessel and the end plate portion 5a of the fixed scroll.
, An oil injection mechanism connected to the oil injection port 22 provided in the hopper. Further, the gas discharge chamber 2a and the electric motor chamber 2d are defined by the frame 11 toward the opposite side from the side end 1a of the sealed container, and an oil reservoir is provided below both chambers.

The frame 11 has a main bearing 26 formed in the center thereof, and a crankshaft (rotating shaft) 82 is supported on the bearing. The eccentric shaft 82a at the tip of the rotating shaft is capable of pivoting movement on the boss 6c. It is inserted like this. Also frame 1
A fixed scroll 5 is fixed to 1 by a plurality of bolts, and an orbiting scroll 6 has a frame 11 by an Oldham mechanism 14 including an Oldham ring and an Oldham key.
The orbiting scroll 6 is formed so as to make a revolving motion without rotating with respect to the fixed scroll 5.

A motor shaft 82b is integrally connected to the rotating shaft 82 in a direction opposite to the compressor portion, and the motor portion 3 is directly connected. A suction pipe 17 (17a, 17a, 17a,
17b) is connected, and the discharge chamber 2a in which the discharge port 10 is open communicates with the electric motor chamber 1d through passages 18a and 18b. The motor room 1d communicates with a discharge pipe 19 that penetrates the casing 1b at the center of the closed container.

The motor room 2d is provided with a motor stator 3a.
And the side walls of the frame and the gap between the motor stator 3a and the motor rotor 3b. An O-ring 21a is provided between the suction pipe 17a and the fixed scroll 5 to seal the high pressure portion and the low pressure portion. A check valve 222 is provided in the suction pipe 17. The check valve 222 prevents reverse rotation of the rotating shaft 82 when the compressor is stopped, and lubricating oil in the sealed container flows out to the low pressure side. It is to prevent that.

A space 77 (hereinafter referred to as a back pressure chamber) surrounded by the scroll compressor unit 2 and the frame 11 is formed on the back surface of the end plate of the orbiting scroll 6.
Reference numeral 7 denotes fine holes 6e and 6f formed in the end plate of the orbiting scroll.
, An intermediate pressure Pb between the suction pressure and the discharge pressure is introduced to apply an axial force for pressing the orbiting scroll 6 against the fixed scroll 5. The lubricating oil 24 is stored at the bottom of the closed container 1 and is sucked up into the oil suction pipe 96d by a differential pressure between the high pressure in the closed container and the intermediate pressure Pb in the back pressure chamber 82. After that, the oil flows through the rotating shaft 82 and is supplied to the slewing bearing 32, the main bearing 26 and the auxiliary bearing 27.

The oil supplied to the bearing portions 26 and 32 is injected into the compression chamber of the scroll wrap through the back pressure chamber 82 through the hole 6 and mixed with the compressed gas, and then discharged together with the discharge gas to the discharge chamber 2a. You. At the bottom of the closed container 1,
An oil take-out pipe 30 is provided for taking out the lubricating oil 24 at the bottom outside the vessel. Further, an oil injection pipe 31 for injecting oil into the compression chamber 8 in the middle of compression of the scroll compressor section 250 is provided in the S cap section 1a of the sealed container 1.

In FIG. 1, the pipe size of the suction pipe 17 and the pipe size of the discharge pipe 19a are set in the range of the ratio shown in the following equation.

[0022]

Zs = 0.0040 to 0.0046 (Equation 7)

[0023]

Zd = 0.0034 to 0.0039 (Equation 8) Here, Zs: ratio of the suction pipe size Bs (inch) to the stroke volume Vth (cm ³ / rev) of the compressor (= Bs / Vth) Zd: Ratio between discharge pipe size Bd (inch) and compressor stroke volume Vth (cm ³ / rev) (= Bd / Vth) Pipe size Bs means the pipe outer diameter in inches. I do. For example, a case of a helium compressor for a rated output of 9 kW of the compressor will be described as an example. Bs = 3/4 inch,
Vth = 180 cm ³ / rev, and Zs = 0.00416, which is in the above (Equation 7). In the discharge pipe, Bd = 5/8 inch and Zd = 0.00347.
And is in the above (Equation 8).

In this area, a flare connection method of the copper pipe becomes possible, and the outer diameter of the compressor becomes compact.
The Zs value of the conventional helium compressor is as follows: Zs = 0.0083
大 き い 0.012, which was a large value. 12H for conventional air conditioning
The suction piping class of the P class is 1 inch, and the piping connection method has an oval flange structure, which increases the cost of parts. In addition, the pipe bending radius increases according to the pipe size, and the external dimension of the compressor unit itself increases. Further, the conventional Zd value is Zd = 0.0062 to 0.011.
It was a large value. Further, as for the oil injection pipe 31 for cooling the working helium gas, the pipe size of the inlet 31a of the oil injection pipe 31 is set in a range of the ratio shown in the following equation.

[0025]

Zo = 0.0026 to 0.0031 (Equation 9) where Zo is the ratio (= Bo) between the oil injection pipe size Bo (inch) and the stroke volume Vth (cm ³ / rev) of the compressor. / Vth) In the case of a helium compressor for a rated output of 9 kW, Bo = 1
/ 2 inch, Vth = 180 cm ³ / rev, and Zo =
0.0027, which is within the range of the above (Equation 9).

Further, since the unified pipe size is advantageous in terms of parts management and productivity, the size of the suction pipe and the size of the discharge pipe are set to be the same, and the pipe size is set in the range of the ratio shown in the following equation.

[0027]

## EQU10 ## Zs = 0.0027 to 0.0046 (Equation 10)

[0028]

Zd = Zs (Equation 11) Further, a scroll compressor for helium having an oil injection pipe 31 for cooling the working helium gas and an oil outlet pipe 51 for guiding the injection oil to the outside from the lower part of the container. In the case where the suction pipe size, the discharge pipe size, and the pipe size of the oil injection pipe and the oil outlet pipe are all the same, and the suction pipe size, the discharge pipe size, and the pipe size of the oil injection pipe and the oil outlet pipe are all the same, The pipe size is set in the range of the ratio shown in the following equation.

[0029]

Zs = 0.0027 to 0.0046 (Equation 12)

[0030]

Zd = Zs = Zo (Equation 13) where Zs is a ratio (= Bs / Vth) between the suction pipe size Bs (inch) and the stroke volume Vth (cm ³ / rev) of the compressor. Ratio between discharge pipe size Bd (inch) and compressor stroke volume Vth (cm ³ / rev) (= Bd / Vth) Zo: Oil injection pipe or oil outlet pipe size Bo (inch) and compressor stroke volume Vth (cm ³ / re
v) (= Bo / Vth) The Zo value of the conventional helium compressor is Zo = 0.0047.
~ 0.008, which is about twice or more the value. If the piping size is relatively two to three times larger, the piping shape in the unit requires an increase in the bending radius, and the unit outer dimensions of the conventional machine are about 1.
About 3 times bigger. When the same pipe thickness is used, the rigidity of the pipe is relatively increased as the pipe size is reduced, which is advantageous in terms of vibration noise.

With the above configuration, when the motor shaft 82b directly connected to the motor rotor 3b rotates and the eccentric shaft 82a rotates eccentrically, the orbiting scroll 6 makes a revolving motion via the revolving bearing 32. Due to this swirling motion, the compression chamber 8 gradually moves to the center and the volume decreases. The working gas enters the suction chamber 5f from the suction pipe 17 through the suction port 16, and the oil lubricating the bearing flows from the frame chamber 11f on the outer peripheral portion of the orbiting scroll end plate of the orbiting scroll 6 into the suction chamber 5f through a minute gap or the like. Mix into the working gas. The working gas containing the oil passing through the bearing and the oil injected from the port 22 is compressed in the compression chamber 8 and discharged from the discharge port 10 to the discharge chamber 2.
a, a part of the oil is separated from the gas in the space 2a, and the gas is passed through the passages 18a, 18b.
to d.

The solid arrows indicate the flow of the working gas, and the broken arrows indicate the flow of the oil. Narrow passages 18a,
The working gas and the oil flowing into the motor room 2d from the space 18b in a large space have a rapid decrease in flow velocity and a change in the flow direction, so that most of the oil contained in the gas is separated, and the working gas is discharged. After flowing into the pipe 19, the oil falls down and stays at the bottom of the closed container 1.

FIG. 2 is a view taken along the line AA of FIG. 11
Reference numerals g and 11k denote oil passages through which the oil in the gas is separated in the discharge chamber 2a and the oil collected below is sent to the motor chamber 2d side.

FIG. 3 is an external view showing an embodiment of an oil-filled hermetic scroll compressor according to the present invention, a lubrication system diagram, and an embodiment of a helium refrigeration apparatus. As shown in FIG. 1, the lubricating oil 24 stored at the bottom of the closed container 1 is supplied to the pressure (discharge pressure Pd) in the closed container 1 and the pressure in the compression chamber 8.
(Pressure lower than the discharge pressure) and the oil discharge pipe 3
The oil flows into the oil take-out pipe 30 from the inflow portion 30a. The oil that has flowed into the oil extraction pipe 30 is
1 to the oil strainer 56 and the oil cooler 33,
After being appropriately cooled here, the oil injection pipe 53,
The gas flows into the compression chamber 8 via the pressure difference 31 and the port 22 by utilizing the differential pressure. 53 is an oil flow control valve. The oil thus injected into the compression chamber plays a role of cooling the working gas and lubricating a sliding portion such as a scroll wrap tip in the compression chamber.

After being compressed together with the working gas, the oil is discharged from the discharge port 10 into the upper chamber 1a, separated from the working gas in the electric motor chamber 2d and accumulated at the bottom of the closed casing 1 as described above. The oil supply to the bearings 32, 26, and 27 is performed by the differential pressure between the pressure in the closed vessel 1 and the pressure (intermediate pressure) Pb in the back pressure chamber 77, and the oil suction pipe 96d and the rotating shaft 82.
This is done via an oil passage inside.

In FIG. 14, the helium gas discharged from the compressor 100 is separated by an oil separator 70 and then cooled by a gas cooler 50. Next, the helium gas is adiabatically expanded in the helium refrigerator 80, and then again in the pipes 340, 3
From 00, the flow returns to the compressor 100 as suction gas. On the other hand, the oil at the bottom of the compressor 100 exits from the oil outlet pipe 51 and is cooled by the oil cooler 33. Next, the oil is depressurized by the oil flow control valve 53 and then injected into the compression chamber 8 during compression via the oil injection pipe 31 to cool the helium gas.
As a region constituting the compressor unit, a one-dot broken line 3 in FIG.
A region surrounded by 80 is obtained. That is, the compressor 100, the oil separator 70, the gas cooler 50, and the oil cooler 33 are main components and are connected by designated pipes.

FIG. 4 is a view as viewed from B in FIG. FIG. 5 is a C view of FIG. 101 is a reed part of the compressor, 45 is
This is an oil level gauge provided to manage the oil level during operation. 5
7 is a power supply unit.

FIG. 6 is a plan view of the fixed scroll 5, and FIG. 7 is a longitudinal sectional view of the fixed scroll 5. The oil injection port 22 can inject cooling oil into both of the compression chambers 8 by one, and is provided at the center position of the wrap groove. The hole diameter d0 is set to a value larger than the wrap thickness t to prevent an oil hammer phenomenon at the time of oil injection.

In FIG. 6 and FIG.
Is a disk-shaped end plate 5a and a wrap 5b formed in series with the end plate 5a to form an involute curve or a curve similar thereto.
A discharge port 10 is provided at the center and a suction port 15 (15a, 15b) is provided at the outer periphery.

8 and 9, the orbiting scroll 6 is formed on a disk-shaped end plate 6a, an upright wrap 6b formed in the same shape as the wrap of the fixed scroll, and an anti-lap surface of the end plate. Boss 6c. The scroll wrap shape shown in FIGS. 6 to 9 has a stroke volume of the compressor (the size of the maximum sealed space) of Vth = 1.
This is an example of 60 cm ³ . Also, changing only the lap height,
Vth can be set to 180 cm ³ . In addition, the fixed scroll 5 and the orbiting scroll 6 having these large scroll tooth shapes are provided, and a cooling oil injection mechanism and an oil outlet pipe for supplying oil to the oil injection mechanism are provided at the bottom of the container. The compressor structure will be described with reference to FIG.

Next, in a scroll compressor for helium using helium gas as a working gas, the scroll wrap portion has a set volume ratio Vr of 1.8 to 2.1 and has a scroll tooth profile dedicated to a low set volume ratio. An embodiment of a helium compressor provided with a fixed scroll and an orbiting scroll meshed with each other will be described. FIG. 8 shows an example of a scroll tooth profile having a set volume ratio Vr of 2.1. Vr is represented by the following equation.

[0042]

[Equation 14]

In FIG. 8, reference numeral 65 denotes an involute curve, and point a is a starting point (λ _S = 2.53 rad). Curve 67 connecting point d and point c is an inner arc curve, and the tip is point a and point c.
The points are connected by a smooth arc curve 66. The curve 68 outside the point d is an involute curve. Dt is given by the following equation.

[0044]

Dt = 2 × εth + t (Equation 15) For example, Dt = 17.5 mm and r3 = 8.75 mm. On the other hand, when r1 = 2.43 mm and the arc diameter at the tip of the wrap is 4.86 mm, the value is the wrap thickness (for example, t
= 4.5 mm). The wrap height is about 40 mm to 45 mm, and the stroke volume of the compressor (the size of the maximum sealed space) is Vth.
= Has secured 160cm ³ ~180cm ^3. in this way,
The thickness of the tip of the wrap is set to be larger than the average thickness t of the wraps 5b and 6b. For this reason, an operational effect that can improve the wrap strength is obtained.

In FIG. 8, points f and g are points at the end of the wrap winding. As an angle, for example, the involute spread angle λ ₁ = 19.3 rad. The wrap winding start angle of Vr = 2.1 specification is λ _S = 2.53 rad. As described above, by setting the volume ratio Vr to be low, a low pressure ratio operation becomes possible, and high performance can be achieved. Further, the lower limit of the operating pressure ratio is set to the conventional operating range, for example, Pd / Ps
= 2.5 to Pd / Ps = 1.7, the operating pressure ratio range can be expanded, while operation can be performed at high suction pressures such as Ps = 15 kg / cm ² G and at low pressure ratio conditions. as a result,
Significant energy savings can be achieved compared to conventional machines. In addition, the life of the rolling bearing can be greatly improved by reducing the bearing load due to the reduction of the motor input Wi accompanying the performance improvement.

FIG. 10 is an explanatory diagram showing a coil temperature measurement position during operation of the electric motor 3. In the present invention, a detailed coil temperature distribution is examined, and as a result, the coil end 3
No. on the g side. It has been found that the region in the upper half of (Equation 6), (Equation 7), (Equation 8), (Equation 9), (Equation 10), and (Equation 12) is the highest temperature region. The coil end part 3
The thermal sensor means 310 is installed in the upper half of g.

FIG. 11 shows an embodiment of a horizontal oil-filled hermetic scroll compressor in which a heat-sensitive sensor means 310 is embedded in the upper half of the coil end 3g on the anti-scroll compressor side of the electric motor in the highest temperature range. FIG. The thermal sensor 310 has a thermistor structure, and detects a resistance value corresponding to the temperature as a signal so that an abnormal temperature of the coil temperature can be detected, and the compressor is forcibly stopped based on the signal. The amount of oil injection can be adjusted, for example, by increasing the degree of opening in conjunction with the throttle means 53. 312 is a lead wire, and 315 is a terminal portion. The present invention mainly relates to the shape of a scroll compressor for helium use, is applicable to a vertical scroll compressor for helium, and is within the scope of the present invention.

[0048]

According to the configuration of the present invention, (1) a large-scale helium scroll compressor having a rated output of 7.5 kW and 9 kW for a large helium compressor and high efficiency can be provided.

(2) The pipe size can be optimized for helium applications where the gas flow rate is small, and the helium compressor and
The overall size of the helium compressor unit can be reduced.

(3) By unifying the pipe size, it is advantageous in terms of parts management and productivity. Therefore, the synergistic effect with the above item (2) can further reduce the weight and reduce the product cost. it can.

(4) Compared with the conventional machine, the unit outer dimensions and the installation area can be greatly reduced, and it is advantageous in terms of low vibration and low noise.

(5) Even if the gas circulation amount is very small compared to the air-conditioning application, the coil end position at which the maximum temperature range is reached
Since the compressor is provided with protection device means for protecting the electric motor, motor burnout can be prevented beforehand, and a highly reliable helium compressor can be provided.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing one embodiment of an oil-filled hermetic scroll compressor according to the present invention.

FIG. 2 is an AA view of FIG. 1;

FIG. 3 is a diagram showing an external appearance, an oil supply system, and a helium refrigeration apparatus showing one embodiment of an oil-filled hermetic scroll compressor according to the present invention.

FIG. 4 is a diagram viewed from a direction B in FIG. 3;

FIG. 5 is a view as seen from a direction C in FIG. 3;

FIG. 6 is a plan view of a fixed scroll 5.

FIG. 7 is a longitudinal sectional view of a fixed scroll 5.

FIG. 8 is a plan view of the orbiting scroll 6;

9 is a vertical sectional view of the orbiting scroll 6. FIG.

FIG. 10 is an explanatory diagram of the electric motor 3.

FIG. 11 is a longitudinal sectional view showing one embodiment of a horizontal oil-filled hermetic scroll compressor of the present invention.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Airtight container, 2a ... Discharge chamber, 2d ... Electric motor room, 3 ... Electric motor part, 3a ... Electric motor stator, 3b ... Electric motor rotor,
5: fixed scroll, 5a: fixed scroll head plate, 5b
... lap, 5f ... suction chamber, 6 ... orbiting scroll, 6a ...
Orbiting scroll head plate, 6b wrap, 6c boss part, 6
p: Central end of orbiting scroll, 8: Compression chamber, 9: Balance weight, 10: Discharge port, 11: Frame, 11g
... Oil passage of frame, 14 ... Oldham mechanism, 15 ... Suction port, 16 ... Rotary shaft, 16a ... Eccentric shaft, 16b ... Electric motor shaft, 16d ... Oil suction pipe, 17 ... Suction pipe, 18a ... Path
18b: passage, 19: discharge pipe, 20: gap, 21: O-ring, 22: port, 23: space, 24: lubricating oil, 26 ...
Main bearing, 27 ... Auxiliary bearing, 30 ... Oil extraction pipe, 30a ...
Inflow section, 31: oil injection pipe, 32: swing bearing, 33: oil cooler, 50: gas cooler, 51: oil pipe, 53: throttle means, 56: oil strainer means, 70
... Oil separating means, 80 ... Refrigerator, 221 ... Oil injection port, 222 ... Check valve, 271 ... Throttle section, 300 ... Suction pipe, 310 ... Oil return pipe, 320 ... Pipe, 330 ... Pipe, 3
40 ... suction pipe.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Yasushi Izu, 390 Muramatsu, Shimizu-shi, Shizuoka Prefecture F-term in Hitachi Air Conditioning Systems Shimizu Production Headquarters (reference) 3H039 AA02 AA06 AA12 BB13 BB25 CC02 CC03 CC05 CC32 CC48

Claims (1)

[Claims] 1. A helium scroll compressor using helium gas as a working gas, swept volume of the compressor a 160cm ³ ~180cm ^3, setting the volume ratio Vr of the scroll wrap portion shown in the following formula 1. A scroll compressor for helium, comprising: a fixed scroll and an orbiting scroll, which are meshed with each other, having a scroll tooth shape of 8 to 2.1. (Equation 1)