JP4754847B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor applied to an air conditioner or the like.

As a compressor applied to an air conditioner or the like, an oil separation chamber for separating lubricating oil mixed in fluid discharged from a compression mechanism from the fluid is provided in the rear housing (discharge chamber side). Is known (see, for example, Patent Document 1).
JP2003-129975A

  In the invention of the above-mentioned Patent Document 1, the lubricating oil separated by the oil separation chamber is once stored in the oil sump chamber and then returned to the suction chamber side through a lubricating oil path (communication path) formed in the fixed side plate. Then, it is supplied to bearings, bushes, and other sliding portions arranged on the suction chamber side to lubricate them.

  In the present invention, the lubricating oil returned to the suction chamber side can be more positively supplied to bearings, bushes, and other sliding parts arranged on the suction chamber side, and when the operating conditions are severe (for example, mounted on a vehicle) In the case of compressors for general use, high pressure tends to rise generally during idling operation at high outside air temperature, and the bearing load becomes severe. As an example of compressor operating conditions, compressor rotation speed is about 1200 (rpm), high pressure about 2.8 ( (MPa) and low pressure of about 0.35 (MPa).) However, an object of the present invention is to provide a compressor that can sufficiently lubricate these members.

The present invention employs the following means in order to solve the above problems.
A compressor according to the present invention includes a housing having a space therein, a compression mechanism disposed in the housing and compressing a fluid taken in the space, and disposed in the housing and discharged from the compression mechanism. An oil separation chamber that separates the lubricating oil mixed in the fluid from the fluid, an oil reservoir chamber that stores the lubricating oil separated by the oil separation chamber, and a communication path that communicates the oil reservoir chamber and the space. A throttle part is provided in the communication path, and the throttle part is provided at the downstream end of the communication path, and is an acceleration part that accelerates the flow of the lubricating oil, A receiving portion for receiving the oil ejected from the outlet of the communication passage is provided at a position facing the opening formed on the outlet side of the communication passage, and the lower end of the receiving portion is lower than the lower end of the opening. When located below Moni, characterized in that it has an inclined surface inclined so as to gradually spaced apart from the opening as it goes to its upper end.
According to such a compressor, the lubricating oil passing through the communication path is accelerated when passing through the throttle portion provided in the communication path, and enters the space from the opening formed on the outlet side of the communication path. It will erupt vigorously.
In addition, according to such a compressor, the lubricating oil passing through the communication path is accelerated when passing through the throttle portion provided at the downstream end of the communication path, and is accelerated to the outlet side of the communication path. From the formed opening, it will spout out into the space vigorously.
Furthermore, according to such a compressor, the lubricating oil jetted out from the opening formed on the outlet side of the communication path into the space flies toward the receiving portion and collides with the receiving portion. It will bounce around (splash) around.
Furthermore, according to such a compressor, the lubricating oil ejected vigorously from the opening formed on the outlet side of the communication path into the space flies toward the inclined surface of the receiving portion. Reflected by an inclined surface and placed in the space, for example, after being stirred (raised) by a balance weight or orbiting scroll, the bearing, eccentric bush, and other sliding parts placed on the suction chamber side of the space Will be supplied.

The scroll compressor according to the present invention is a scroll compressor having a fixed scroll, a turning scroll, a drive unit that drives the turning scroll, and a housing that forms a drive unit space for housing the drive unit. And a communication part having a throttle part, and a receiving part for receiving the oil ejected from the low-pressure side opening of the communication path. The receiving portion is provided at a position facing the opening of the housing, and the receiving portion communicates with the drive unit space. The receiving portion has a lower end located below the lower end of the opening, and as it goes to the upper end. It has an inclined surface which is inclined so as to be gradually separated from the opening .
According to such a scroll type compressor, after the oil whose pressure is adjusted by the throttle portion is ejected from the opening, the oil is supplied to the receiving portion and is then supplied to the driving portion.
Moreover, according to such a scroll type compressor, the oil which flew by the inclined surface splashes to the drive part side, so that it can be supplied to the drive part more reliably.

The communication path includes a low-pressure side throttle portion having the opening and a high-pressure side throttle portion located on a higher pressure side than the low-pressure side throttle portion, and the flow resistance of the high-pressure side throttle portion is the low-pressure side throttle portion. It is good also as a structure larger than this flow path resistance.
According to such a scroll compressor, the decompressed oil can be held between the high-pressure side throttle part and the low-pressure side throttle part, so that it can be removed from the opening of the low-pressure side throttle part without causing oil shortage. Oil can be ejected.

Moreover, the cross-sectional area A of the low-pressure side throttle part is
A2 ≦ C2 · (π2ΔP2 / (8192μ2g)) · (D8 / l2) · (h / L2))
(Where C is the flow coefficient, ΔP is the differential pressure, μ is the actual viscosity of the lubricating oil, g is the gravitational acceleration, D is the hydraulic diameter of the throttle in the high pressure side throttle, and l is the length of the throttle in the high pressure side throttle. , H is a head difference (perpendicular distance between the center of the opening and the bottom of the receiving part) , and L is a distance (horizontal distance between the end face of the receiving part and the opening ))
It is preferable that the configuration satisfies the above.
According to such a scroll type compressor, it is possible to provide a compressor in which oil ejected from the opening reliably reaches the receiving portion by determining the area of the low-pressure side throttle portion regardless of the position where the communication path is provided.

Further, the low-pressure side throttle part is provided so as to have a circular cross section, and the inner diameter d of the circular cross section is:
d4 ≦ C2 · (ΔP2 / (512μ2g)) · (D8 / l2) · (h / L2))
(Where C is the flow coefficient, ΔP is the differential pressure, μ is the actual viscosity of the lubricating oil, g is the gravitational acceleration, D is the hydraulic diameter of the throttle in the high pressure side throttle, and l is the length of the throttle in the high pressure side throttle. , H is a head difference (perpendicular distance between the center of the opening and the bottom of the receiving part) , and L is a distance (horizontal distance between the end face of the receiving part and the opening ))
It is preferable that the configuration satisfies the above.
According to such a scroll compressor, regardless of the position where the communication passage is provided, the oil can reliably reach the receiving portion by determining the inner diameter of the low-pressure side throttle portion.

  According to the compressor of the present invention, the lubricating oil returned to the suction chamber side can be more positively supplied to the bearings, bushes, and other sliding portions arranged on the suction chamber side when the operating conditions are severe. (For example, there is an effect that these members and the like can be sufficiently lubricated even at high load idling (rotation speed: about 1200 (rpm), high pressure: about 2.8 (MPa), low pressure: about 0.35 (MPa)).

Hereinafter, an embodiment of a compressor according to the present invention (hereinafter referred to as a “scroll type compressor”) will be described with reference to the drawings. Of course, the present invention is not limited to this.
As shown in FIG. 1, the scroll compressor 10 according to the present embodiment includes a housing 11 having a sealed space m therein, and a refrigerant gas (fluid) disposed in the housing 11 and taken into the sealed space m. The main components are a scroll compression mechanism 12 that compresses the scroll compression mechanism 12, a rotary shaft 13 that drives the scroll compression mechanism 12, and a drive unit that drives the scroll compression mechanism 12 to revolve.

  The housing 11 includes a front housing 14 and a rear housing 15, which are combined and then coupled with a plurality of bolts (not shown) to form a sealed space m inside. ing. Reference numeral 16 denotes a single O-ring that seals the joint between the front housing 14 and the rear housing 15 to keep the sealed space m sealed. A thrust plate 14a that matches the end surface is provided on the end surface of the front housing 14, and a hole (notch) (not shown) corresponding to a receiving portion 38 to be described later is formed in the thrust plate 14a.

A suction port (not shown) for sucking refrigerant gas is formed on the front side of the rear housing 15 so as to communicate with the sealed space m. A scroll compression mechanism is provided on the upper rear side of the rear housing 15. 12, a discharge port 15a is formed through which compressed refrigerant gas is discharged after the lubricating oil in the refrigerant gas is separated by an oil separation chamber (not shown). Further, an oil reservoir chamber 18 (oil storage portion) that stores the lubricating oil separated by the oil separation chamber is formed on the discharge side (high pressure side) of the rear housing 15.
The oil separation chamber only needs to have an oil separation function such as a centrifugal separation type so that the separated oil is led to the oil reservoir chamber 18.

The scroll compression mechanism 12 includes a fixed scroll 21 and a turning scroll 22.
The fixed scroll 21 includes a fixed end plate 21a and a spiral wall body 21b erected on the inner surface thereof, and a discharge port 21c is formed at the center of the fixed end plate 21a. The discharge port 21c is opened and closed by a discharge valve (not shown) attached to the rear surface (back surface) of the fixed end plate 21a via a bolt (not shown).
A communication path (lubricating oil path) 23 that connects the bottom of the oil reservoir 18 and the suction side bottom of the sealed space m is formed at the lower end of the fixed scroll 21. The filter 24 and the spiral pin 25 for flow rate adjustment are arranged from the upstream side. The communication passage 23 and the spiral pin 25 will be described in more detail later.

The orbiting scroll 22 includes an orbiting end plate 22a and a spiral wall body 22b standing on the inner surface thereof. An eccentric bush 31 is rotatably fitted in a boss 22c erected on the outer surface of the swivel end plate 22a via a needle bearing 32, and the rotary shaft 13 is inserted into a hole formed in the eccentric bush 31. An eccentric pin 13a that protrudes from the end is fitted. A plurality of compression chambers C are formed by causing the fixed scroll 21 and the orbiting scroll 22 to be eccentric from each other by a predetermined distance and engaged with each other while shifting the angle by 180 degrees.
An Oldham ring (rotation prevention mechanism) 33 is provided between the orbiting scroll 22 and the front housing 14, and the orbiting scroll 22 does not rotate around the eccentric bush 31 when the rotating shaft 13 is rotated. It is like that. Therefore, when the rotary shaft 13 is rotated, the orbiting scroll 22 does not rotate but only performs a revolving orbiting motion. Further, the eccentric bush 31 is provided with a balance weight 34 so as to cancel the centrifugal force accompanying the revolution of the orbiting scroll 22.

The rotating shaft 13 is a rotor shaft that rotates about its axis by a driving mechanism (not shown) such as an engine or an electric motor, and the above-described eccentric pin 13a having an eccentric axis is projected from the tip thereof. The rotating shaft 13 is supported by a first bearing 35 and a second bearing 36 provided on the front housing 14 side so as to be rotatable around the axis.
The driving force from the engine, the electric motor, or the like is transmitted or not transmitted to the rotary shaft 13 via an electromagnetic clutch (not shown).
Reference numeral 37 denotes a single O-ring that seals the joint between the fixed scroll 21 and the rear housing 15 to keep the sealed space m sealed.

  The above-described elements constitute a drive unit that drives the orbiting scroll to revolve. Specifically, in the scroll compressor 10 having such a structure, the electromagnetic clutch is engaged to provide the engine. And the driving force from the electric motor or the like is transmitted to the rotary shaft 13 and the rotary shaft 13 is rotated. This rotation is rotated to the orbiting scroll 22 of the scroll compression mechanism 12 via the eccentric pin 13a, the eccentric bush 31 and the boss 22c. Communicated. The orbiting scroll 22 is configured to perform a revolving orbiting motion on a circular orbit having a revolution orbiting radius as a radius while being prevented from rotating by the Oldham ring 33.

Then, the refrigerant gas enters the sealed space m of the housing 11 through the suction port, and is sucked into the compression chamber C of the scroll compression mechanism 12 through a path not shown. Then, as the volume of the compression chamber C decreases due to the revolving orbiting motion of the orbiting scroll 33, the refrigerant gas reaches the center while being compressed, and the refrigerant containing the lubricating oil is led from the discharge port 21c to the oil separation chamber. , Swirled along the inner wall surface of the oil separation chamber. As a result, the lubricating oil mixed in the refrigerant falls down while turning along the inner wall surface of the oil separation chamber by the centrifugal separation action and is stored in the oil reservoir chamber 18, while the lubricating oil is separated. The refrigerant is discharged to the outside through the inside of the inner cylinder and the discharge port 15a of the rear housing 15.
Therefore, in the present embodiment, from the viewpoint of the refrigerant pressure, the side including the discharge port 21c and the oil sump chamber 18 in the scroll compressor 10 is the high pressure side, and the side including the suction port and the first bearing 35 is the low pressure side. .

Now, the communication path 23 and the spiral pin 25 will be described in detail.
The communication passage 23 communicates the oil reservoir chamber 18 provided on the high pressure side in the scroll compressor 10 and the low pressure side, and further has a large diameter having substantially the same inner diameter as the outer diameter of the spiral pin 25. A portion 23a and a small-diameter portion (throttle portion) 23b having an inner diameter smaller than the inner diameter of the large-diameter portion 23a. Portion) 23b is formed in the order of the large diameter portion 23a and the small diameter portion 23b from the upstream side (oil reservoir chamber 18 side).
The spiral pin 25 is a member having a substantially cylindrical shape, and both end portions are formed with tapered portions 25a, and a spiral groove (hereinafter, “ 25c ”(referred to as“ spiral groove ”). The spiral pin 25 is disposed on the upstream side (the oil reservoir chamber 18 side) in the large diameter portion 23a. The lubricating oil that has passed through the filter 24 once flows out into the large diameter portion 23a located on the downstream side of the spiral pin 25 through the spiral groove 25c, and then flows out to the suction side bottom of the sealed space m through the small diameter portion 23b. (Squirting).

Here, the throttle portion 23b has an end opening 23c of the communication passage 23 that opens toward the orbiting scroll 22, but the throttle portion formed by the spiral pin 25 interposes a space formed by the large diameter portion 23a. Thus, it is possible to realize an independent throttle configuration in which different flow path resistances can be set.
More specifically, the main purpose is to form the high-pressure side restricting portion as a pressure / flow rate adjusting portion for returning the oil from the high-pressure side to the low-pressure side by the above-described spiral groove, while jetting the oil from the communication passage 23. The low-pressure side restricting portion as the pressure / flow rate adjusting portion is formed by the small diameter portion 23b described above. For this reason, in the present embodiment, the flow path resistance of the high-pressure side throttle section is made larger than the flow path resistance of the low-pressure side throttle section, and oil in an appropriate pressure state is reliably supplied from the high pressure side to the low pressure side. .

  A (lubricating oil) receiving portion 38 is provided at a position facing the opening 23c provided at the downstream end of the small diameter portion 23b. The receiving portion 38 is a notch (recess) formed in the inner wall surface of the front housing 14 located at the suction side bottom of the sealed space m. As shown in FIG. 1, the bottom surface of the receiving portion 38 is a slope having a substantially constant width formed so as to gradually approach the opening 23c of the small diameter portion 23b from the radially inner side to the radially outer side. The lower end is formed so as to be positioned below the lower end of the opening 23c of the small diameter portion 23b.

  FIG. 2 is a diagram schematically showing a spiral groove 25 c, a large diameter portion 23 a, and a small diameter portion 23 b that serve as a flow path for the lubricating oil that has passed through the filter 24. That is, the lubricating oil that has passed through the filter 24 sequentially passes through the spiral groove 25c, the large-diameter portion 23a, and the small-diameter portion 23b, and then toward the receiving portion 38 that is separated from the opening 23c by the head difference h and the distance L. Will be ejected.

Hereinafter, the two throttle parts will be described in detail. As shown in FIG. 2, in the spiral groove (flow rate adjusting throttle) 25c functioning as the high-pressure side throttle part and the small-diameter part (acceleration throttle) 23b functioning as the low-pressure side throttle part, the spiral groove 25c is more in the flow path. The resistance is set to be large. The oil stored in the oil reservoir 18 on the high-pressure side in the spiral groove 25c is adjusted from the high pressure to the low pressure, and the flow rate of oil return is adjusted. Here, when the flow rate is Q, from the Hagen-Poiseuille equation, Q = C · (πD ⁴ ΔP / 128 μl) (1)
It is expressed.
Here, C is a flow coefficient, D is a hydraulic diameter of the high-pressure side throttle part, ΔP is a differential pressure between the high pressure and the low pressure, μ is an actual viscosity of oil, and l is a length of the throttle of the high-pressure side throttle part.
In addition, because of the positional correlation between the opening 23c and the receiving portion 38, the oil ejected from the opening 23c reaches the receiving port beyond the head difference h and the distance L. It is necessary to satisfy the following conditional expression.
A ² ≦ (2Q ² / g) · (h / L ² )
Here, Q is a flow rate obtained from the equation (1), and g is a gravitational acceleration.
As a result, the following equation is derived from the equations (1) and (2).
A ² ≦ C ² · (π ² ΔP ² / (8192 μ ² g)) · (D ⁸ / l ² ) · (h / L ² )) ·· (3)
Where C is the flow coefficient, ΔP is the differential pressure, μ is the actual viscosity of the lubricating oil, g is the gravitational acceleration, D is the hydraulic diameter of the high pressure side throttle, l is the length of the high pressure side throttle, and h is the head difference. , L is the distance.
For example, from the formula (3), when the diaphragm of the low pressure side diaphragm part has a circular cross section,
d ⁴ ≦ C ² (ΔP ² / (512 μ ² g)) (D ⁸ / l ² ) (h / L ² )) (4)
It is better to set d such that

Next, the head difference (vertical distance: shortest distance) h between the center of the opening 23c and the bottom surface of the receiving portion 38 is, for example, 2.2 (mm), and the horizontal distance L between the end surface of the receiving portion 38 and the opening 23c is, for example, 12.2 (mm). ) And when the operating conditions are severe (for example, when high load idling (revolution speed 1200 (rpm), high pressure 2.45 (MPa), low pressure 0.31 (MPa) is assumed, what is the diameter d2 of the opening 23c?) For example, it will be examined whether the lubricating oil that has protruded from the opening 23c reaches the receiving portion 38.
The flow rate of the lubricating oil passing through the opening 23c is 298.666 (mm ³ / s) obtained from the Hagen-Poiseuille equation (Equation (1)).

First, when the diameter d2 of the opening 23c is 1.5 (mm), the sectional area of the opening 23c is 1.77 (mm ² ), and the flow velocity from the opening 23c is 1686.60 (mm / s). When this flow velocity (1668.60 (mm / s)) is divided by the horizontal distance L (12.2 (mm)) between the end face of the receiving portion 38 and the opening 23c, the lubricant that has jumped out of the opening 23c moves the horizontal distance L. It is possible to obtain a time t (0.007 (s)) required for. If the value of t is substituted into the free fall equation (h1 = 1/2 · g · t ² ), a result of h1 = 0.262 (mm) can be obtained. This is a vertical distance in which the lubricating oil that has jumped out of the opening 23c while moving the horizontal distance L falls due to gravity, and is a head difference h (2.2 (mm)) between the center of the opening 23c and the bottom surface of the receiving portion 38. This means that the lubricating oil that is sufficiently smaller than the opening 23c can reach the receiving portion 38 sufficiently.

  Further, when the same calculation is performed for the case where the diameter d2 of the opening 23c is 3 (mm), the results of t = 0.029 (s) and h1 = 4.194 (mm) can be obtained. It can be seen that the lubricating oil jumping out from the opening 23c cannot reach the receiving portion 38. As described above, as for the narrowing of the small diameter portion 23b, the smaller diameter is advantageous in that the reaching distance becomes large. However, as a limit of reducing the diameter, it is at a level that does not affect the throttling of the spiral groove 25c, and by machining or the like. The size should be designed so that it can be easily opened.

Further, in the embodiment shown in FIG. 1, the opening 23c is intermittently opened and closed by the turning end plate 22a of the rotating orbiting scroll 22, and the opening angle of the opening 23c is, for example, 160 degrees. The opening time T is 0.022 (s). In this case, the opening 23c is opened, and the opening 23c is closed after the lubricating oil that has jumped out of the opening 23c having the above-described hole diameter reaches the receiving portion 38. In such a case, if the arrival time t is large, the oil ejected from the opening 23c is blocked by the orbiting scroll before reaching the receiving port 38, so that the arrival time t is smaller than the opening time T. It is advantageous.
Further, in the embodiment of the present application, even when the above-mentioned orbiting scroll closes the opening 23c for the large-diameter portion 23a in the communication path, oil passing through 25c from the high pressure side is stored in the large-diameter portion 23a. When the orbiting scroll opens the opening 23c, a larger amount of oil can be ejected.

As described above, according to the scroll compressor 10 according to the present embodiment, when the lubricant separated by the oil separation chamber is returned to the suction chamber, the lubricant is directed from the opening 23c toward the receiving portion 38. Will erupt vigorously. The lubricating oil that has jumped out of the opening 23c collides with the receiving portion 38 (bounces), bounces back (splashes) around, is agitated (raised) by the balance weight 34 and the orbiting scroll 30, and is disposed on the suction chamber side. The bearings 32 and 35, the eccentric bush 31 and other sliding parts are directly supplied. As a result, for example, when the operating conditions are severe (for example, when idling at a high load (rotation speed: about 1200 (rpm), high pressure: about 2.8 (MPa), low pressure: about 0.35 (MPa)), these members are sufficiently lubricated. Thus, seizure of bearings, eccentric bushes and other sliding parts can be prevented.
Further, a part of the lubricating oil agitated (squeezed up) by the balance weight 34 and the orbiting scroll 30 is mixed in the refrigerant gas before compression, whereby the lubrication of the compression mechanism 12 and the sealed space m Sealing is performed.
In the embodiment of the present application, the case of a spiral pin provided with a spiral groove has been described as the high-pressure side restricting portion, but it may naturally be a capillary tube or a simple pore.

In addition, the scroll type compressor mentioned above can also be not only an open type as mentioned above but a semi-hermetic type or a hermetic type scroll type compressor.
Moreover, the scroll compressor mentioned above can be used not only for vehicle installation as described above but also for stationary installation.
Furthermore, the compressor is not limited to the scroll type compressor as described above, and may be a swash plate compressor, a reciprocating compressor, or the like.
Furthermore, the compressor is not limited to the horizontal type as described above, but may be a vertical type.

  The average inner diameter d of the communication path described in the claims and the means for solving the problems is the average inner diameter of the entire length of the spiral groove 25c, the large diameter portion 23a, and the small diameter portion 23b. The differential pressure ΔP is the difference between the high pressure and the low pressure, and the hydraulic diameter D is a value obtained by dividing the average cross-sectional area of the communication passage by four times, and dividing the wet crossover length by The aperture length l is the total length of the spiral groove 25c, the large diameter portion 23a, and the small diameter portion 23b, and the flight distance L is the horizontal distance between the end face of the receiving portion 38 and the opening 23c. In addition, the actual viscosity of the lubricating oil is an actual viscosity when passing through the throttle of the high-pressure side throttle portion, and it should be considered when the refrigerant is dissolved in the oil.

It is a section construction diagram showing one embodiment of a compressor by the present invention. It is the schematic diagram which drew typically the spiral groove, the large diameter part, and the small diameter part which are shown in FIG.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Scroll type compressor 11 Housing 12 Scroll compression mechanism 14 Front housing 15 Rear housing 17 Oil separation chamber,
18 Oil sump chamber,
23 Communication passage 23b Small diameter part (throttle part)
23c Opening 38 Receiving part m Sealed space

Claims (5)

A housing having a space inside;
A compression mechanism that is disposed within the housing and compresses a fluid taken into the space;
An oil separation chamber that is disposed in the housing and separates lubricating oil mixed in the fluid discharged from the compression mechanism from the fluid;
An oil sump chamber for storing lubricating oil separated by the oil separation chamber;
A compressor including a communication passage communicating the oil reservoir chamber and the space;
A throttle portion is provided in the communication path,
The throttle portion is provided at the downstream end of the communication path, and is an acceleration portion that accelerates the flow of the lubricating oil,
A receiving portion for receiving oil ejected from the outlet of the communication path is provided at a position facing the opening formed on the outlet side of the communication path,
The receiving portion has a lower end located below the lower end of the opening, and an inclined surface that is inclined so as to be gradually separated from the opening as it goes to the upper end. Machine. In a scroll compressor having a fixed scroll, a turning scroll, a drive unit that drives the turning scroll, and a housing that forms a drive unit space for housing the drive unit,
The oil storage portion provided on the high pressure side in the scroll compressor and the low pressure side are communicated with each other, and a communication passage having a throttle portion is provided.
A receiving portion that receives oil ejected from the low-pressure side opening of the communication passage is provided at a position facing the opening portion of the housing, and the receiving portion communicates with the drive portion space,
The receiving part has a slanting surface whose lower end is located below the lower end of the opening and which is inclined so as to be gradually separated from the opening as it goes to the upper end. . The communication path includes a low-pressure side throttle portion having the opening, and a high-pressure side throttle portion located on a higher pressure side than the low-pressure side throttle portion,
3. The scroll compressor according to claim 2, wherein a flow path resistance of the high pressure side throttle section is larger than a flow path resistance of the low pressure side throttle section. The cross-sectional area A of the low-pressure side throttle part is
A ² ≦ C ² · (π ² ΔP ² / (8192 μ ² g)) · (D ⁸ / l ² ) · (h / L ² ))
(Where C is the flow coefficient, ΔP is the differential pressure, μ is the actual viscosity of the lubricating oil, g is the gravitational acceleration, D is the hydraulic diameter of the throttle in the high pressure side throttle, and l is the length of the throttle in the high pressure side throttle. , H is a head difference (perpendicular distance between the center of the opening and the bottom of the receiving part) , and L is a distance (horizontal distance between the end face of the receiving part and the opening ))
The scroll compressor according to claim 3, wherein: The low-pressure side throttle part is provided so as to have a circular cross section,
The inner diameter d of the circular cross section is
d ⁴ ≦ C ² · (ΔP ² / (512 μ ² g)) · (D ⁸ / l ² ) · (h / L ² ))
(Where C is the flow coefficient, ΔP is the differential pressure, μ is the actual viscosity of the lubricating oil, g is the gravitational acceleration, D is the hydraulic diameter of the throttle in the high pressure side throttle, and l is the length of the throttle in the high pressure side throttle. , H is a head difference (perpendicular distance between the center of the opening and the bottom of the receiving part) , and L is a distance (horizontal distance between the end face of the receiving part and the opening ))
The scroll compressor according to claim 3, wherein:

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