JPWO2020148857A1 - Scroll compressor - Google Patents

Abstract

The scroll compressor is provided at the lower end of the drive shaft, and as the drive shaft rotates, the oil in the oil storage portion is supplied to the sliding portion of the drive shaft through the oil supply flow path formed in the drive shaft. It includes an oil pump and a back pressure frame arranged in a back pressure chamber facing the back surface of the swing scroll. The back pressure chamber has a first back pressure chamber that communicates with the space inside the closed container and becomes a high pressure, and a second back pressure chamber in which an intermediate pressure fluid or an intermediate pressure oil is introduced to apply an intermediate pressure to the back surface of the swing scroll. It is partitioned by a back pressure chamber and a back pressure frame.

Description

The present invention relates to a high pressure shell type scroll compressor.

A conventional scroll compressor includes a compression mechanism unit, an electric motor for driving the compression mechanism unit, and a drive shaft for transmitting the rotational force of the electric motor to the compression mechanism unit in a closed container. The compression mechanism unit has a compression chamber formed by meshing spiral bodies of a fixed scroll and a swing scroll, and the volume of the compression chamber is reduced by swinging the swing scroll with respect to the fixed scroll. To compress the fluid.

In a high-pressure shell type scroll compressor in which the inside of the closed container has a high pressure, the oil in the oil storage section provided at the bottom of the closed container is subjected to a differential pressure lubrication method to the compression mechanism section located at the upper part of the closed container. (For example, see Patent Document 1). In the differential pressure refueling method, a space with an intermediate pressure that is lower than the high pressure in the closed container is formed on the back surface opposite to the spiral teeth in the swing scroll, and the differential pressure with the oil storage part that becomes high pressure is used. It is a method of refueling.

Japanese Patent No. 2560849

The differential pressure refueling method of Patent Document 1 has a problem that the amount of refueling becomes excessive under the condition that the pressure difference between the low pressure when the fluid is sucked into the container and the high pressure in the container is large.

Further, in a scroll compressor, if there is a gap between the tip of each of the spiral teeth of the swing scroll and the fixed scroll and the base plate of the scroll on the opposite side, fluid leakage occurs and the compressor Performance is reduced. Therefore, it is required to press the swing scroll against the fixed scroll side with an appropriate pressure to eliminate the gap.

The present invention has been made in view of these points, and in a high-pressure shell type scroll compressor, excessive refueling is suppressed under a condition where the pressure difference between high and low pressure is large, and an appropriate pressure is applied to the fixed scroll side of the swing scroll. It is an object of the present invention to provide a scroll compressor capable of pressing with.

The scroll compressor according to the present invention includes a fixed base plate portion and a fixed scroll having fixed spiral teeth provided on the fixed base plate portion, and a swing base plate portion and a swing provided on the rocking base plate portion. A swing scroll having spiral teeth, and the swing spiral teeth are combined with the fixed spiral teeth of the fixed scroll to form a compression chamber, a drive shaft for driving the swing scroll, and a swing base plate portion of the swing scroll. A fixed frame that forms a back pressure chamber on the back surface opposite to the swinging spiral teeth, and a container that stores the fixed scroll, swing scroll, drive shaft, and fixed frame, and has an oil storage unit that stores oil. It has a closed container whose inside becomes high pressure together with the oil storage part by the fluid compressed from low pressure to high pressure in the compression chamber and is provided at the lower end of the drive shaft, and the oil storage part is provided as the drive shaft rotates. An oil pump that supplies the oil of the above to the sliding part of the drive shaft through the oil supply flow path formed in the drive shaft, and a back pressure frame arranged in the back pressure chamber facing the back surface of the swing scroll. The back pressure chamber has a first back pressure chamber that communicates with the space inside the closed container and becomes high pressure, and an intermediate pressure fluid or intermediate pressure oil is introduced to act an intermediate pressure on the back surface of the swing scroll. It is partitioned by a back pressure frame and a second back pressure chamber.

According to the present invention, a back pressure frame is arranged in a back pressure chamber to form a first back pressure chamber, and the first back pressure chamber is communicated with a space in a closed container to have a high pressure similar to that of an oil storage unit. Therefore, the pressure difference between the first back pressure chamber and the oil storage unit becomes 0, differential pressure refueling is not performed, and the differential pressure dependence of the refueling amount can be suppressed. As a result, excessive refueling under conditions where the pressure difference between high and low pressure is large can be suppressed. Then, the back pressure chamber is divided into a high-pressure first back pressure chamber and a second back pressure chamber into which an intermediate pressure fluid or an intermediate pressure oil is introduced to become an intermediate pressure by a back pressure frame. Two types of back pressure, high pressure and intermediate pressure, can be applied to the back surface of the swing scroll. As a result, the degree of freedom in design is increased, and the swing scroll can be pressed against the fixed scroll side with an appropriate pressure.

It is a schematic vertical sectional view which shows the whole of the scroll compressor which concerns on Embodiment 1 of this invention. It is a schematic cross-sectional view of AA of FIG. It is a schematic cross-sectional view of BB of FIG. It is a schematic cross-sectional view of CC of FIG. It is explanatory drawing of the flow of fluid and oil in the scroll compressor which concerns on Embodiment 1 of this invention. It is explanatory drawing of the pressing force which presses a rocking scroll toward a fixed scroll side by a back pressure acting on a rocking scroll. It is a figure explaining the difference of the tooth tip load when the back pressure frame is provided and when it is not provided. It is a schematic vertical sectional view of the scroll compressor which concerns on Embodiment 2 of this invention. It is a schematic vertical sectional view of the scroll compressor which concerns on Embodiment 3 of this invention. It is a perspective view which shows the upper part of the drive shaft of the scroll compressor which concerns on Embodiment 3 of this invention. It is a figure which shows the shape around the drive shaft of the scroll compressor which concerns on Embodiment 3 of this invention. It is a schematic vertical sectional view which enlarged the main part of the scroll compressor which concerns on Embodiment 4 of this invention. It is explanatory drawing of the force acting on the valve body in the scroll compressor which concerns on Embodiment 4 of this invention. It is a figure which shows the modification of the scroll compressor which concerns on Embodiment 4 of this invention. It is a schematic vertical sectional view which enlarged the main part of the scroll compressor which concerns on Embodiment 5 of this invention. It is a schematic vertical sectional view which enlarged the main part of the scroll compressor which concerns on Embodiment 6 of this invention.

Hereinafter, the scroll compressor according to the embodiment of the present invention will be described with reference to the drawings and the like. Here, in the following drawings including FIG. 1, those having the same reference numerals are the same or equivalent thereto, and are common to the whole texts of the embodiments described below. The form of the component represented in the entire specification is merely an example, and is not limited to the form described in the specification. In addition, the height of the pressure is not determined in relation to the absolute value, but is relatively determined in the state and operation of the system, the device, and the like.

[Embodiment 1]
(composition)
The scroll compressor according to the first embodiment of the present invention will be described, and FIG. 1 is a schematic vertical sectional view showing the entire scroll compressor according to the first embodiment of the present invention. FIG. 2 is a schematic cross-sectional view taken along the line AA of FIG. FIG. 3 is a schematic cross-sectional view taken along the line BB of FIG. FIG. 4 is a schematic cross-sectional view taken along the line CC of FIG. FIG. 5 is an explanatory diagram of fluid and oil flow in the scroll compressor according to the first embodiment of the present invention. In FIG. 5, white arrows indicate fluid flow and solid arrows indicate oil flow. It should be noted that each figure is schematically drawn, and the present invention is not limited to the illustrated form.

The scroll compressor 100 of the first embodiment is a high-pressure shell type scroll compressor in which most of the internal space of the closed container 10 has a high pressure. The scroll compressor 100 has a function of sucking a low-pressure fluid such as a refrigerant and discharging it in a high-pressure state, and compresses the compression mechanism unit 90, the electric motor 8, and the rotational force of the electric motor 8 in the closed container 10. It houses the drive shaft 7 and the like that are transmitted to the mechanism unit 90. As shown in FIG. 1, in the closed container 10, the compression mechanism portion 90 is arranged at the upper portion and the electric motor 8 is arranged at the central portion. The bottom of the closed container 10 is an oil storage section 10d for storing oil.

A suction pipe 11 into which a low-pressure fluid flows in and a discharge pipe 12 in which a compressed high-pressure fluid flows out are connected to the closed container 10. The suction pipe 11 penetrates the closed container 10 and is fitted into the fixed scroll 1 described later of the compression mechanism unit 90. The end of the suction pipe 11 is located in the suction space 90a on the outer periphery of the compression mechanism 90, and causes the suction space 90a to suck a low-pressure fluid. Further, the closed container 10 is provided with a terminal (not shown) through which electricity passes when supplying electric power to the electric motor 8.

The closed container 10 has an upper space 10a above the compression mechanism 90 and a lower space 10b below the compression mechanism 90. In the closed container 10, the upper space 10a and the lower space 10b from which the fluid compressed by the compression mechanism 90 is discharged are the gap between the inner peripheral surface of the closed container 10 and the compression mechanism 90 and the components of the electric motor 8. It communicates through gaps between them. Therefore, the inside of the closed container 10 is filled with the high-pressure fluid discharged from the compression mechanism unit 90 to have a high pressure. The oil storage section 10d provided at the bottom of the closed container 10 is in contact with the lower space 10b, and the oil storage section 10d is also maintained at a high pressure similar to that of the lower space 10b and the upper space 10a, and is stored in the oil storage section 10d. Oil is also kept at high pressure.

A fixed frame 3 and an auxiliary frame 5 are arranged inside the closed container 10. The fixed frame 3 is located between the compression mechanism unit 90 and the electric motor 8. The fixed frame 3 supports the compression mechanism unit 90 and forms a back pressure chamber 3a described later with the swing scroll 2 described later of the compression mechanism unit 90. The auxiliary frame 5 is located below the motor 8. The fixed frame 3 and the auxiliary frame 5 are fixed to the inner peripheral surface of the closed container 10 by shrink fitting, welding, or the like.

The electric motor 8 is composed of a stator 8a fixed to the closed container 10 and a rotor 8b rotatably arranged inside the stator 8a. The rotor 8b is fixed to the outer circumference of the drive shaft 7, and rotates when the stator 8a is energized to rotate the drive shaft 7.

The compression mechanism unit 90 is a mechanism for compressing a fluid, and is configured by combining a fixed scroll 1 and a swing scroll 2. The fixed scroll 1 has a disk-shaped fixed base plate portion 1a and a plate-shaped spiral tooth (hereinafter referred to as “fixed spiral tooth”) 1b provided on the fixed base plate portion 1a. The fixed scroll 1 is fastened to the fixed frame 3 by bolts (not shown) at the outer peripheral portion of the fixed base plate portion 1a and fixed to the closed container 10. A discharge port 1d for discharging a compressed and high-pressure fluid is formed near the center of the fixed base plate portion 1a of the fixed scroll 1. The compressed and high-pressure fluid is discharged from the discharge port 1d into the upper space 10a in the closed container 10.

The oscillating scroll 2 is provided on the disk-shaped oscillating base plate portion 2a and the oscillating base plate portion 2a, and has a plate-shaped spiral tooth having substantially the same shape as the fixed spiral tooth 1b (hereinafter, "oscillating spiral tooth"). (Referred to as) 2b. A hollow cylindrical bearing portion 2c is formed in the central portion of the surface (hereinafter referred to as the back surface) of the rocking base plate portion 2a opposite to the swing spiral tooth 2b. An eccentric shaft 7a, which will be described later, provided at the upper end of the drive shaft 7 is inserted into the bearing portion 2c. An oldham mechanism 6 is arranged between the rocking scroll 2 and the fixed frame 3, and the rocking scroll 2 is driven by the rotation of the drive shaft 7, and the swinging motion is regulated by the olddam mechanism 6. do. The swing scroll 2 slides on the thrust surface 2f, which is a part of the back surface of the swing base plate portion 2a, with respect to the thrust receiving surface of the back pressure frame 4, which will be described later.

A back pressure chamber 3a is formed on the back surface of the swing scroll 2. The back pressure chamber 3a is a space for applying a pressure for pressing the swing scroll 2 to the fixed scroll 1 on the swing scroll 2, and is formed in a space in a recess formed on the upper surface of the fixed frame 3. ..

The fixed scroll 1 and the swing scroll 2 are arranged in the closed container 10 in a state where the fixed spiral tooth 1b and the swing spiral tooth 2b are meshed with each other. By combining the fixed spiral tooth 1b and the swinging spiral tooth 2b, a compression chamber 13 is formed between the fixed spiral tooth 1b and the swinging spiral tooth 2b. The compression chamber 13 moves from the outer peripheral side to the inner peripheral side by the rocking scroll 2 swinging with respect to the fixed scroll 1, and the volume is gradually reduced to perform the compression operation.

The drive shaft 7 rotates with the rotation of the rotor 8b, and transmits the rotational driving force of the electric motor 8 to the compression mechanism unit 90. The main shaft 7b on the upper part of the drive shaft 7 is rotatably supported by a main bearing provided at the center of the fixed frame 3. An eccentric shaft 7a eccentric with respect to the central shaft of the drive shaft 7 is provided at the upper end of the drive shaft 7. The eccentric shaft 7a is inserted into the bearing portion 2c of the swing scroll 2. The lower auxiliary shaft 7c of the drive shaft 7 is rotatably supported by an auxiliary bearing provided at the center of the auxiliary frame 5. In this way, the drive shaft 7 is rotatably supported by the main bearing and the sub bearing. Further, the drive shaft 7 is provided with a balancer 7d located in the back pressure chamber 3a to balance the imbalance caused by the swinging motion of the swinging scroll 2. The balancer 7d has a tubular outer peripheral surface centered on the central axis of the drive shaft 7.

A positive displacement oil pump 20 is provided at the lower end of the drive shaft 7 to suck up the lubricating oil stored in the oil storage portion 10d according to the rotation of the drive shaft 7. The oil pump 20 is attached to the lower end of the drive shaft 7 via a thrust bearing 9. The thrust bearing 9 is held by the thrust holder 40. The lubricating oil sucked up by the oil pump 20 is supplied to the compression mechanism 101 and sliding parts such as the main bearing via the oil supply flow path 7e formed inside the main shaft 7b. The oil supply flow path 7e includes a vertical hole that penetrates the drive shaft 7 in the axial direction, and a plurality of horizontal holes that extend in the radial direction of the drive shaft 7 from the vertical hole toward the outer peripheral surface of the drive shaft 7. Lubricating oil for the oil storage portion 10d is supplied to each bearing which is a sliding portion of the drive shaft 7 through an axial hole and a lateral hole.

Here, the oil flow path formed in the fixed frame 3 will be described.
The fixed frame 3 has a first oil flow path 31 that returns the oil accumulated in the back pressure chamber 3a to the oil storage unit 10d, and a second oil flow path 31 that supplies the oil accumulated in the back pressure chamber 3a to the suction space 90a. An oil flow path 32 is formed. Although the second oil flow path 32 communicates with the first oil flow path 31 in FIG. 1, it may communicate with the back pressure chamber 3a independently of the first oil flow path 31. Further, a part of the outer circumference of the fixed frame 3 is cut out to form an oil return flow path 81 between the fixed frame 3 and the closed container 10. The oil return flow path 81 is a flow path for returning the oil supplied to the compression mechanism unit 90 to the oil storage unit 10d. The oil return flow path 81 is provided in the closed container 10 at a position where it does not merge with the flow path through which the fluid flows. As a result, it is possible to prevent the oil flowing out of the oil return flow path 81 and returning to the oil storage unit 10d from being wound up by the fluid and flowing out together with the fluid to the outside of the compressor. As a result, it is possible to prevent the oil inside the compressor from being depleted and poor lubrication, and the reliability can be improved.

The operation of the scroll compressor 100 configured as described above will be briefly described.
When electric power is supplied to the electric motor 8 and the drive shaft 7 rotates, the swing scroll 2 swings with its rotation regulated by the Oldham mechanism 6. The gaseous fluid sucked into the closed container 10 from the suction pipe 11 flows into the compression chamber 13 of the compression mechanism unit 90. The compression chamber 13 into which the fluid has flowed in reduces the volume while moving from the outer peripheral portion toward the center along with the swinging motion of the swing scroll 2, and compresses the fluid.

The compressed fluid is discharged from the discharge port 1d provided near the center of the fixed scroll 1 to the upper space 10a in the closed container 10. The fluid discharged into the upper space 10a passes through the fluid flow path 82 (see FIGS. 2 and 3), which is a gap between the inner peripheral surface of the closed container 10 and the outer peripheral surface of the fixed scroll 1, and the motor 8 is installed. It flows into the lower space 10b in the closed container 10. The fluid flowing into the lower space 10b descends through the gap formed in the electric motor 8, folds back at the auxiliary frame 5, rises, and is discharged from the discharge pipe 12 to the outside of the closed container.

Next, the flow of oil in the scroll compressor 100 will be described.
When electric power is supplied to the electric motor 8 and the drive shaft 7 rotates, the oil stored in the oil storage unit 10d is pumped up by the oil pump 20 provided at the lower end of the drive shaft 7, and the oil supply flow path in the drive shaft 7 is pumped up. It is supplied to the sliding portion of the drive shaft 7 through 7e. The oil that has flowed out from the upper end opening of the vertical hole of the oil supply flow path 7e and the oil that has flowed out from the horizontal hole flow into the back pressure chamber 3a in a high pressure state. A part of the oil that has flowed into the back pressure chamber 3a flows out to the lower space 10b via the first oil flow path 31 and is returned to the oil storage section 10d. The other oil that has flowed into the back pressure chamber 3a is supplied to the suction space 90a of the compression mechanism unit 90 via the second oil flow path 32.

[Suppression of differential pressure dependence of refueling amount]
In the conventional patent document 1, the pressure in the back pressure chamber 3a is set to an intermediate pressure between high pressure and low pressure, and oil is supplied to a bearing or the like by the pressure difference between the high pressure of the oil storage portion 10d and the intermediate pressure of the back pressure chamber 3a. ing. In such a differential pressure refueling method, since the amount of refueling depends on the pressure difference, excessive refueling occurs when the pressure difference is large. Therefore, in the first embodiment, the differential pressure dependence is suppressed by refueling with the positive displacement oil pump 20 instead of adopting the differential pressure refueling method. However, the differential pressure dependence cannot be suppressed simply by using the oil pump 20. An appropriate gap is provided between the plurality of parts constituting the oil pump 20. Therefore, if there is a pressure difference between the back pressure chamber 3a and the oil storage unit 10d, the oil in the oil storage unit 10d rises through the gap of the oil pump 20 and passes through the oil supply flow path 7e in the drive shaft 7. It is supplied to each sliding part and differential pressure lubrication is performed.

Therefore, in the first embodiment, the back pressure chamber 3a is communicated with the lower space 10b via the first oil flow path 31, and the pressure difference between the back pressure chamber 3a and the oil storage portion 10d is set to 0. As a result, the pressure in the back pressure chamber 3a becomes as high as that in the oil storage unit 10d. Since the back pressure chamber 3a and the oil storage portion 10d have the same high pressure, oil supply due to the pressure difference is not performed, and oil supply to the sliding portion and the like is only the operation of the oil pump 20 accompanying the rotation of the drive shaft 7. Is done by. As described above, the first oil flow path 31 not only functions as a flow path for returning the oil in the back pressure chamber 3a to the oil storage unit 10d, but also communicates the inside of the back pressure chamber 3a with the lower space 10b to obtain oil. It also has a function of increasing the pressure similar to that of the storage unit 10d.

The amount of oil supplied by the oil pump 20 depends on the number of revolutions of the drive shaft 7. Therefore, there is a possibility of over-refueling at high rpm. Therefore, in the first embodiment, in order to suppress excessive refueling at a high rotation speed, the flow path resistance of the second oil flow path 32 is made larger than the flow path resistance of the first oil flow path 31. The amount of oil supplied to the suction space 90a of the compression mechanism unit 90 through the second oil flow path 32 is smaller than the amount of oil returned to the oil storage unit 10d through the first oil flow path 31.

The flow path resistance is represented by a value obtained by dividing the flow path length L by the cross-sectional area A. Therefore, the relationship between the "cross-sectional area A1 and length L1 of the first oil flow path 31" and the "cross-sectional area A2 and length L2 of the second oil flow path 32" is set to "L1 / A1> L2 / A2". There is. By adjusting the flow path resistance of the first oil flow path 31 and the flow path resistance of the second oil flow path 32 in this way, excessive refueling at a high rotation speed can be suppressed, and an appropriate amount can be obtained in a wide range of rotation speeds. Refueling can be realized.

Further, in order to supply an appropriate amount of oil to the suction space 90a without causing a loss in the oil pump 20, the resistance when the oil passes through the eccentric shaft 7a and the main shaft 7b of the drive shaft 7 may be reduced. Therefore, "the cross-sectional area A2 and the length L2 of the second oil flow path 32" and "the cross-sectional area A3 of the gap between the eccentric shaft 7a of the drive shaft 7 and the bearing portion 2c of the swing scroll 2 and the shaft of the gap" It is desirable that the relationship with "length L3 in the direction" is "L2 / A2> L3 / A3". See FIG. 3 for cross-sectional area A3 and length L3.

[New issues associated with higher pressure in the back pressure chamber]
In the first embodiment, as described above, by setting the back pressure chamber 3a to the same high pressure as the oil storage unit 10d and setting the pressure difference to 0, the difference pressure dependence of the amount of refueling can be suppressed, but the back pressure chamber can be suppressed. A new problem arises by increasing the pressure inside 3a.

A new problem is that the high pressure inside the back pressure chamber 3a causes a high back pressure to act on the back surface of the swing scroll 2, and the force for pressing the swing scroll 2 against the fixed scroll 1 becomes excessive. Is. If the pressing force becomes excessive, the tips of the spiral teeth of the swing scroll 2 and the fixed scroll 1 come into contact with the base plate of the scroll on the opposite side, causing abnormal wear or seizure, resulting in reliability. Sexual problems arise.

[Characteristics of the present embodiment]
Therefore, in the first embodiment, the back pressure frame 4 is arranged in the back pressure chamber 3a, and the back pressure frame 3a is divided into a chamber that communicates with the lower space 10b in the closed container 10 and becomes a high pressure chamber. A chamber for applying an intermediate pressure is separately formed on the back surface of the swing scroll 2. Hereinafter, a specific configuration will be described.

The back pressure frame 4 is formed in an annular plate shape extending in a direction orthogonal to the drive shaft 7, and is arranged so as to face the back surface of the rocking base plate portion 2a of the rocking scroll 2. As shown in FIG. 4, a pair of annular walls 4d facing each other at intervals in the radial direction are formed on the inner peripheral side and the outer peripheral side of the back pressure frame 4, and between the pair of annular walls 4d. The sealing material 4c is housed in the groove. The tip surface of the sealing material 4c is in contact with the back surface of the rocking base plate portion 2a of the rocking scroll 2, and is partitioned from the high-pressure first back pressure chamber 3aa into the back pressure chamber 3a to form an annular second. A back pressure chamber 3ab is formed. The second back pressure chamber 3ab has an intermediate pressure by communicating with the compression chamber 13 in the middle of compression by the bleeding holes 2d formed in the swing base plate portion 2a of the swing scroll 2. In this way, the back pressure frame 4 divides the inside of the back pressure chamber 3a into a high-pressure first back pressure chamber 3aa and an intermediate pressure second back pressure chamber 3ab, and the swing base plate portion of the swing scroll 2. Two different types of back pressure are applied to the back surface of 2a.

The back pressure frame 4 is fixed to the fixed frame 3, and the tip surface of the annular wall 4d serves as a thrust receiving surface that slides with the thrust surface 2f of the rocking scroll 2 during the rocking motion of the rocking scroll 2. There is.

The pressure at which the tips of the spiral teeth of the swing scroll 2 and the fixed scroll 1 come into contact with the base plate portion of the scroll on the opposite side is the magnitude of the pressure introduced into the second back pressure chamber 3ab and the second. It depends on the size of the pressure receiving area of the back pressure chamber 3ab. In other words, the load acting on the tooth tip (hereinafter referred to as the tooth tip load) can be changed depending on the magnitude of the pressure introduced into the second back pressure chamber 3ab and the pressure receiving area of the second back pressure chamber 3ab. Hereinafter, this point will be described in comparison with the case where the back pressure frame 4 is provided and the case where the back pressure frame 4 is not provided.

FIG. 6 is an explanatory diagram of a pressing force that presses the swing scroll toward the fixed scroll side by the back pressure acting on the swing scroll.
The tooth tip load Ftip is a force obtained by subtracting the force Fdown that tries to separate the swing scroll 2 from the fixed scroll 1 from the force that pushes the swing scroll 2 toward the fixed scroll 1.

Fdown is a resultant force of the force due to the gas pressure of the compression mechanism unit 90 and the gravity acting on the swing scroll 2, and is substantially unchanged as long as the shape of the swing scroll 2 does not change.

On the other hand, the force Fup that pushes the swing scroll 2 toward the fixed scroll 1 differs depending on whether the back pressure frame 4 is provided or not, and is represented by the following.

(A) When the back pressure frame 4 is provided Fup = (Pd × B1) + (Pm × B2)
here,
Pd: Pressure of the first back pressure chamber 3aa Pm: Pressure of the second back pressure chamber 3ab B1: Pressure receiving area of the first back pressure chamber 3aa B2: Pressure receiving area of the second back pressure chamber 3ab

(B) When the back pressure frame 4 is not provided Fup = Pd × (B1 + B2)

When the back pressure frame 4 is not provided, the pressure that determines the Fup is only the pressure Pd of the first back pressure chamber 3aa. On the other hand, when the back pressure frame 4 is provided, the pressure Pm of the second back pressure chamber 3ab is involved in addition to the pressure Pd of the first back pressure chamber 3aa. Therefore, the tooth tip load can be changed by adjusting the pressure Pm of the second back pressure chamber 3ab and the pressure receiving area B2. That is, by providing the back pressure frame 4 and applying two different types of back pressure to the back surface of the swing scroll 2, the degree of freedom in design is increased. Therefore, the pressure in the second back pressure chamber 3ab can be designed to be an appropriate pressure for reducing gas leakage and friction in the compression chamber 13.

Specifically, the tooth tip load is reduced by increasing the pressure receiving area B2 of the second back pressure chamber 3ab. In order to increase the pressure receiving area B2 of the second back pressure chamber 3ab, the relationship between the inner radius Rf of the back pressure frame 4 (see FIG. 4) and the outer radius Rb of the balancer 7d (see FIG. 3) is described as "inside the back pressure frame". The radius Rf <balancer outer radius Rb "may be set. Therefore, by appropriately setting the pressure receiving area B2 of the second back pressure chamber 3ab, it is possible to achieve both an appropriate pressure setting for reducing gas leakage and friction in the compression chamber 13 and a rotational balance when the compressor is driven. ..

The following figure shows the result of comparing the tooth tip load in the case of (a) and the case of (b).

FIG. 7 is a diagram illustrating a difference in tooth tip load between the case where the back pressure frame is provided and the case where the back pressure frame is not provided. In FIG. 7, the dot portion shows the tooth tip load due to the pressure Pd, and the hatched portion shows the tooth tip load due to the pressure Pm.
As is clear from FIG. 7, when (a) the back pressure frame 4 is provided, the tooth tip load can be reduced as compared with the case where (b) the back pressure frame 4 is not provided. In (b), seizure or the like occurs when the allowable load is exceeded. When the tooth tip load is 0 or less, a gap is formed in the tooth tip and the efficiency is lowered. Therefore, it is ideal that the tooth tip load is slightly higher than 0. In (a), the tooth tip load is slightly above 0, which is ideal.

As described above, according to the first embodiment, the pressure difference between the back pressure chamber 3a and the oil storage unit 10d is set to 0 in order to prevent differential pressure refueling. Specifically, the back pressure chamber 3a communicates with the lower space 10b, which is a space in contact with the oil storage unit 10d in the closed container 10. This communication is performed in the first oil flow path 31 provided in the fixed frame 3. Then, refueling is performed by a positive displacement oil pump 20 provided at the lower end of the drive shaft 7. As a result, differential pressure refueling is not performed, and excessive refueling can be suppressed under conditions where the pressure difference between high and low pressure is large. As a result, the compressor loss due to the fluid sucked into the compression mechanism 90 being heated by the oil excessively supplied into the compression mechanism 90 can be reduced, and the efficiency of the compressor can be improved. Further, in the air conditioner to which the scroll compressor 100 is applied, the cooling / heating capacity can be improved.

Then, in the first embodiment, the back pressure frame 4 is arranged in the back pressure chamber 3a facing the back surface of the swing scroll 2. The back pressure chamber 3a is divided into a first back pressure chamber 3aa that becomes a high pressure and a second back pressure chamber 3ab that applies an intermediate pressure to the back surface of the swing scroll 2 by the back pressure frame 4. By providing the back pressure frame 4 in the back pressure chamber 3a in this way, it is possible to apply two types of back pressure, high pressure and intermediate pressure, to the back surface of the swing scroll 2, and the degree of freedom in design is increased. Therefore, the swing scroll 2 can be pressed against the fixed scroll 1 side with an appropriate pressure.

In the first embodiment, the fixed scroll includes a first oil flow path 31 that communicates the first back pressure chamber 3aa and the lower space 10b, and a closed container in which the first back pressure chamber 3aa and the low-pressure fluid are sucked. A second oil flow path 32 that communicates with the suction space 90a in the 10 is formed. As a result, the oil in the back pressure chamber 3a can be supplied to the suction space 90a and returned to the oil storage unit 10d.

In the first embodiment, the relationship between the "cross-sectional area A1 and length L1 of the first oil flow path 31" and the "cross-sectional area A2 and length L2 of the second oil flow path 32" is "L1 / A1>. It is "L2 / A2". As a result, excessive refueling at high speed can be suppressed.

In the first embodiment, the cross-sectional area of the gap between the "cross-sectional area A2 and length L2 of the second oil flow path 32" and the "eccentric shaft 7a of the drive shaft 7 and the bearing portion 2c of the swing scroll 2" The relationship between A3 and the axial length L3 of the gap is defined as "L2 / A2> L3 / A3". As a result, the oil pump 20 can supply an appropriate amount of oil to the suction space 90a without causing a loss.

In the first embodiment, the relationship between the inner radius Rf of the back pressure frame 4 and the outer radius Rb of the balancer 7d is “back pressure frame inner radius Rf <balancer outer radius Rb”. As a result, it is possible to suppress the load acting on the swinging spiral tooth 2b and to achieve both rotational balance.

In the first embodiment, the rocking base plate portion 2a of the rocking scroll 2 is formed with an air extraction hole 2d that connects the compression chamber 13 during compression and the second back pressure chamber 3ab. As a result, the fluid of the intermediate pressure during compression is introduced into the second back pressure chamber 3ab, and the second back pressure chamber 3ab can be set to the intermediate pressure.

[Embodiment 2] Piping for oil return Embodiment 2 will be described with reference to FIG. FIG. 8 is a schematic vertical sectional view of the scroll compressor according to the second embodiment of the present invention. In FIG. 8, white arrows indicate fluid flow and solid arrows indicate oil flow. Hereinafter, the configuration in which the second embodiment is different from the first embodiment will be mainly described.

In the second embodiment, the oil return pipe 80 for communicating the first oil flow path 31 and the oil storage unit 10d is provided in the first embodiment shown in FIG. Although the pipe 80 is arranged outside the closed container 10 in this example, the pipe 80 may be arranged inside the closed container 10.

The pipe 80 directly returns the oil excessively pumped by the oil pump 20 at the time of high rotation from the first oil flow path 31 to the oil storage unit 10d. As a result, the oil that has flowed out of the first oil flow path 31 does not merge with the fluid flow in the lower space 10b until it is returned to the oil storage section 10d. Therefore, it is possible to prevent the oil from being wound up by the fluid and flowing out together with the fluid to the outside of the compressor. As a result, it is possible to prevent the oil inside the compressor from being depleted and poor lubrication, and the reliability can be improved.

As described above, according to the second embodiment, the same effect as that of the first embodiment can be obtained, and the pipe 80 that communicates the first oil flow path 31 and the oil storage portion 10d is provided. The effect of is obtained. That is, it is possible to prevent the oil returned from the first oil flow path 31 to the oil storage unit 10d from being wound up by the fluid and flowing out together with the fluid to the outside of the compressor, and the reliability can be improved.

[Embodiment 3] Slider drive shaft 7 The third embodiment will be described with reference to FIGS. 9, 10 and 11. FIG. 9 is a schematic vertical sectional view of the scroll compressor according to the third embodiment of the present invention. FIG. 10 is a perspective view showing the upper part of the drive shaft of the scroll compressor according to the third embodiment of the present invention. FIG. 11 is a diagram showing the shape around the drive shaft of the scroll compressor according to the third embodiment of the present invention. Hereinafter, the configuration in which the third embodiment is different from that of the first embodiment will be mainly described.

The scroll compressor 100 of the third embodiment includes a slider 70 with respect to the first embodiment. The slider 70 is provided so that the swinging spiral tooth 2b of the swinging scroll 2 is always in contact with the fixed spiral tooth 1b of the fixed scroll 1 when the swinging scroll 2 revolves. The slider 70 has a balancer portion 70a and a shaft portion 70b, and the balancer portion 70a has the same function as the balancer 7d of the first embodiment. The shaft portion 70b is formed in a tubular shape and is interposed between the bearing portion 2c of the swing scroll 2 and the eccentric shaft 7a of the drive shaft 7. The slider 70 transmits the rotational force of the drive shaft 7 to the swing scroll 2 to cause the swing scroll 2 to revolve eccentrically.

The eccentric shaft 7a is composed of a pair of opposing flat surface portions 7aa and an arc portion 7ab connecting both ends of the flat surface portions 7aa, and is slidably fitted into the slider hole 70c of the slider 70. The slider hole 70c has a shape in which a pair of flat surface portions 7aa of the eccentric shaft 7a are stretched in the plane direction.

(Slider function)
The slider 70 slides outward in the radial direction following the flat surface portion 7aa of the eccentric shaft 7a due to the centrifugal force acting on the balancer portion 70a. Since the center of rotation of the swing scroll 2 is equal to the center in the axial direction of the slider 70, when the slider 70 slides in the radial direction, the swing scroll 2 also slides in the same manner. At this time, the swing scroll 2 slides together with the slider 70 until the tooth side surface of the swing spiral tooth 2b comes into contact with the tooth side surface of the fixed spiral tooth 1b. As a result, when the swing scroll 2 revolves, the fixed spiral tooth 1b of the fixed scroll 1 and the swing spiral tooth 2b of the swing scroll 2 are always in contact with each other, and fluid leakage from the compression chamber 13 is suppressed. NS.

As described above, according to the third embodiment, the same effect as that of the first embodiment can be obtained, and the slider 70 has the following effects. That is, when the swing scroll 2 slides in the radial direction by the slider 70, the compression motion is performed in a state where the tooth side surface of the swing spiral tooth 2b is in contact with the tooth side surface of the fixed spiral tooth 1b. Therefore, it is possible to prevent the fluid in the process of compression in the compression chamber 13 or the discharge pressure fluid in the center of the compression chamber 13 from leaking from the radial gap between the fixed spiral tooth 1b and the swing spiral tooth 2b. Compression efficiency is improved.

[Embodiment 4] The pressure in the second back pressure chamber depends on the spring force. The fourth embodiment will be described with reference to FIG. FIG. 12 is an enlarged schematic vertical sectional view of a main part of the scroll compressor according to the fourth embodiment of the present invention. Hereinafter, the configuration in which the fourth embodiment is different from the first embodiment will be mainly described.

In the scroll compressor 100 of the fourth embodiment, the air extraction hole 2d of the swing scroll 2 in the scroll compressor 100 shown in the first embodiment is removed. Further, in the scroll compressor 100 of the fourth embodiment, the oil of the first oil flow path 31 is supplied to the second back pressure chamber 3ab by communicating the second back pressure chamber 3ab and the second oil flow path 32. The bleed air flow path 33 is formed in the fixed frame 3. A pressure adjusting mechanism 60 for adjusting the pressure of the second back pressure chamber 3ab is arranged in the second oil flow path 32. The pressure adjusting mechanism 60 includes a valve body 60a that opens and closes the second oil flow path 32, and the valve body 60a is urged by a spring 61 in the direction of closing the second oil flow path 32.

FIG. 13 is an explanatory diagram of the force acting on the valve body in the scroll compressor according to the fourth embodiment of the present invention.
The pressure Ps of the suction space 90a acts downward on the valve body 60a, and the pressure Pm of the second back pressure chamber 3ab acts upward. Further, the pressure due to the spring force F, that is, the pressure F / A obtained by dividing the spring force F by the pressure receiving area of the valve body 60a acts downward on the valve body 60a. Therefore, when the "differential pressure ΔP between the pressure Pm and the pressure Ps" is smaller than the pressure F / A due to the spring force F, the second oil flow path 32 is closed by the valve body 60a as shown in FIG. .. On the other hand, when the "differential pressure ΔP between the pressure Pm and the pressure Ps" is larger than the pressure F / A due to the spring force F, the valve body 60a is lifted upward with respect to the urging force of the spring 61, and the second oil flow path 32 opens. When the second oil flow path 32 opens, the second back pressure chamber 3ab communicates with the suction space 90a via the bleed air flow path 33 and the second oil flow path 32. That is, when the pressure Pm of the second back pressure chamber 3ab becomes larger than Ps + F / A, the second oil flow path 32 opens and the pressure of the second back pressure chamber 3ab is released. Therefore, the pressure Pm of the second back pressure chamber 3ab is maintained at Ps + F / A.

As described above, according to the fourth embodiment, the same effect as that of the first embodiment can be obtained, and the pressure of the second back pressure chamber 3ab depends on the volume change of the fluid in the first embodiment. It can be changed to force dependence, increasing the degree of freedom in design. As a result, the load acting on the swing spiral teeth 2b of the swing scroll 2 can be appropriately set, and the pressure operation range of the scroll compressor 100 can be expanded.

In addition, although the pressure adjusting mechanism 60 was configured to include the valve body 60a urged by the spring 61 in FIG. 12, it may be configured as shown in FIG. 14 below.

FIG. 14 is a diagram showing a modified example of the scroll compressor according to the fourth embodiment of the present invention.
In this modification, the pressure adjusting mechanism 60 is configured to include a reed valve having a valve body 60c. With this configuration, the number of members can be reduced, and with a simpler structure, the same effect as the configuration of FIG. 12 can be obtained.

[Embodiment 5] Movable frame, third back pressure chamber Embodiment 5 will be described with reference to FIG. FIG. 15 is an enlarged schematic vertical sectional view of a main part of the scroll compressor according to the fifth embodiment of the present invention. Hereinafter, the configuration in which the fifth embodiment is different from that of the first embodiment will be mainly described.

In the fifth embodiment, the movable frame 50 that floats by using the intermediate pressure in the compression chamber 13 as the back pressure and presses the swing scroll 2 against the fixed scroll 1 is arranged in the fixed frame 3. Details will be described below.

The movable frame 50 is arranged on the back side of the swing scroll 2 so as to be movable in the axial direction with respect to the fixed frame 3. The movable frame 50 has a large-diameter tubular portion 50d and a small-diameter tubular portion 50e provided below the tubular portion 50d. The inside of the tubular portion 50d of the movable frame 50 is a back pressure chamber 3a, and a third oil flow path 50c communicating the back pressure chamber 3a and the first oil flow path 31 is formed in the tubular portion 50d. There is. A recess is formed on the upper surface of the tubular portion 50d, and the back pressure frame 4 is arranged in the recess. In the fifth embodiment, the upper surfaces of the back pressure frame 4 and the movable frame 50 are thrust receiving surfaces that slide with the thrust surface 2f of the rocking base plate portion 2a of the rocking scroll 2.

The outer surface of the tubular portion 50e of the movable frame 50 is surrounded by the inner surface of the upper tubular portion 3c of the fixed frame 3. Further, the outer surface of the tubular portion 50e is surrounded by the inner surface of the lower tubular portion 3d of the fixed frame 3. An annular seal portion 11a and a seal portion 11b are provided between the tubular portion 50d and the upper tubular portion 3c, and a seal portion 11c is provided between the tubular portion 50e and the lower tubular portion 3d. ing. As a result, a third back pressure chamber 50a partitioned from other spaces is formed on the back side of the movable frame 50.

A communication hole 50b penetrating in the axial direction is formed in the tubular portion 50d of the movable frame 50. The upper end side of the communication hole 50b opens on the surface of the swing scroll 2 facing the swing base plate portion 2a, and the lower end side communicates with the third back pressure chamber 50a.

An air extraction hole 2g is formed in the rocking base plate portion 2a of the rocking scroll 2. The bleeding hole 2g penetrates the rocking base plate portion 2a from the fixed scroll 1 side to the movable frame 50 side. The extraction hole 2g is a narrow hole for supplying the fluid of the compression chamber 13 during compression to the third back pressure chamber 50a. The opening on the movable frame 50 side of the extraction hole 2g is arranged at a position where the circular locus of the opening always fits inside the movable frame 50 during operation, and the opening on the upper end side of the communication hole 50b provided in the movable frame 50. Communicate with the department constantly or intermittently. As a result, the intermediate pressure in the compression chamber 13 is constantly or intermittently guided to the third back pressure chamber 50a through the extraction hole 2g and the communication hole 50b. The pressure in the third back pressure chamber 50a acts as the back pressure of the movable frame 50, and the movable frame 50 floats due to the back pressure to push the swing scroll 2 against the fixed scroll 1.

As described above, according to the fifth embodiment, the same effect as that of the first embodiment can be obtained, and the three back pressure chambers 3aa, the second back pressure chamber 3ab, and the third back pressure chamber 50a are obtained. Back pressure can be applied to the swing scroll 2. As a result, the load acting on the swing spiral tooth 2b of the swing scroll 2 can be appropriately set, the sliding loss between the thrust surface 2f of the swing scroll 2 and the thrust receiving surface of the movable frame 50 is reduced, and the scroll tooth The previous sliding loss can be reduced. As a result, the pressure operating range of the compressor can be further expanded.

[Embodiment 6] Movable frame + slider Embodiment 6 will be described with reference to FIG. FIG. 16 is an enlarged schematic vertical sectional view of a main part of the scroll compressor according to the sixth embodiment of the present invention.

The sixth embodiment is a combination of the third embodiment and the fifth embodiment, and has a configuration in which the slider 70 of the third embodiment is provided in the fifth embodiment provided with the movable frame 50.

According to the sixth embodiment, the same effects as those of the third embodiment and the fifth embodiment can be obtained.

In the sixth embodiment, the embodiment 3 and the fifth embodiment are combined, but in addition to this combination, the scroll compressor is configured by appropriately combining the characteristic configurations of the respective embodiments. You may. Further, the modification described in the fourth embodiment can be similarly applied to the configuration combined with the other embodiments.

1 Fixed scroll, 1a Fixed base plate part, 1b Fixed spiral tooth, 1d discharge port, 2 Swing scroll, 2a Swing base plate part, 2b Swing swirl tooth, 2c Bearing part, 2d Air extraction hole, 2f Thrust surface, 2g Extraction hole, 3 Fixed frame, 3a back pressure chamber, 3aa 1st back pressure chamber, 3ab 2nd back pressure chamber, 3c upper tubular part, 3d lower tubular part, 4 back pressure frame, 4c sealant, 4d annular wall 5, Auxiliary frame, 6 Oldham mechanism, 7 Drive shaft, 7a Eccentric shaft, 7aa Flat surface, 7ab Arc, 7b Main shaft, 7c Sub-shaft, 7d Balancer, 7e Refueling flow path, 8 Electric, 8a Fixture, 8b Rotor , 9 thrust bearing, 10 sealed container, 10a upper space, 10b lower space, 10d oil storage, 11 suction pipe, 11a seal, 11b seal, 11c seal, 12 discharge pipe, 13 compression chamber, 19 fixed frame, 20 Oil pump, 31 1st oil flow path, 32 2nd oil flow path, 33 Extraction flow path, 40 Thrust holder, 50 Movable frame, 50a 3rd back pressure chamber, 50b communication hole, 50c 3rd oil flow path, 50d Cylindrical part, 50e tubular part, 60 pressure adjustment mechanism, 60a valve body, 60c valve body, 61 spring, 70 slider, 70a balancer part, 70b shaft part, 70c slider hole, 80 piping, 81 oil return flow path, 82 Fluid flow path, 90 compression mechanism, 90a suction space, 100 scroll compressor.

The scroll compressor according to the present invention includes a fixed scroll having a fixed base plate portion and fixed spiral teeth provided on the fixed base plate portion, and a swing provided on the swing base plate portion and the rocking base plate portion. A swing scroll that has spiral teeth and the swing spiral teeth are combined with the fixed spiral teeth of the fixed scroll to form a compression chamber, a drive shaft that drives the swing scroll, and a swing base plate portion of the swing scroll. A fixed frame that forms a back pressure chamber on the back surface opposite to the swinging spiral teeth, and a container that stores the fixed scroll, swing scroll, drive shaft, and fixed frame, and has an oil storage section that stores oil. It has a closed container whose inside becomes high pressure together with the oil storage part by the fluid compressed from low pressure to high pressure in the compression chamber and is provided at the lower end of the drive shaft. An oil pump that supplies the oil of the above to the sliding part of the drive shaft through the oil supply flow path formed in the drive shaft, and a back pressure frame arranged in the back pressure chamber facing the back surface of the swing scroll. The back pressure chamber has a first back pressure chamber that communicates with the space inside the closed container and becomes high pressure, and an intermediate pressure fluid or intermediate pressure oil is introduced to act an intermediate pressure on the back surface of the swing scroll. The second back pressure chamber is partitioned by a back pressure frame, and the fixed frame includes a first oil flow path that communicates the first back pressure chamber and the space in contact with the oil storage portion in the closed container. The second oil flow path that communicates the first back pressure chamber and the suction space in the closed container in which the low-pressure fluid is sucked, and the second oil flow path and the second back pressure chamber that communicate with each other. An air extraction flow path for introducing the oil in the flow path into the second back pressure chamber is formed, and the second oil flow path has a valve body for opening and closing the second oil flow path, and the second A pressure adjusting mechanism for adjusting the pressure in the back pressure chamber is provided .

Claims (10)

A fixed scroll having a fixed base plate portion and fixed spiral teeth provided on the fixed base plate portion, and
It has a rocking base plate portion and swinging spiral teeth provided on the rocking base plate portion, and the swinging spiral teeth are combined with the fixed spiral teeth of the fixed scroll to form a compression chamber. Scrolling and
The drive shaft that drives the swing scroll and
A fixed frame that forms a back pressure chamber on the back surface of the rocking base plate portion of the rocking scroll opposite to the rocking spiral teeth.
A container for storing the fixed scroll, the swing scroll, the drive shaft, and the fixed frame, which has an oil storage unit for storing oil, and is compressed and discharged from a low pressure to a high pressure in the compression chamber. A closed container with a high pressure inside together with the oil storage
Provided at the lower end of the drive shaft, the oil in the oil storage portion is supplied to the sliding portion of the drive shaft by passing through an oil supply flow path formed in the drive shaft as the drive shaft rotates. Oil pump and
A back pressure frame arranged in the back pressure chamber facing the back surface of the swing scroll is provided.
The back pressure chamber is intermediate between the first back pressure chamber, which communicates with the space in the closed container and becomes high pressure, and the back pressure chamber, in which the fluid of intermediate pressure or the oil of intermediate pressure is introduced and the back pressure chamber is introduced. A scroll compressor partitioned by the back pressure frame in a second back pressure chamber on which pressure is applied. The fixed frame
A first oil flow path that communicates the first back pressure chamber with a space in the closed container that is in contact with the oil storage portion.
The scroll compressor according to claim 1, wherein a second oil flow path communicating the first back pressure chamber and the suction space in the closed container into which the low-pressure fluid is sucked is formed. The second aspect of claim 2, wherein the relationship between the cross-sectional area A1 and the length L1 of the first oil flow path and the cross-sectional area A2 and the length L2 of the second oil flow path is "L1 / A1> L2 / A2". Scroll compressor. A bearing portion into which an eccentric shaft formed at an end portion of the drive shaft is inserted is formed on the back surface of the swing scroll.
The cross-sectional area A2 and length L2 of the second oil flow path, and the cross-sectional area A3 of the gap between the eccentric shaft of the drive shaft and the bearing portion of the swing scroll, and the axial length of the gap. The scroll compressor according to claim 2 or 3, wherein the relationship with L3 is "L2 / A2> L3 / A3". It is arranged in the first back pressure chamber, has a tubular outer peripheral surface, and is provided with a balancer that balances the imbalance caused by the swinging motion of the swinging scroll.
The one according to any one of claims 1 to 4, wherein the relationship between the inner radius Rf of the back pressure frame and the outer radius Rb of the balancer is "back pressure frame inner radius Rf <balancer outer radius Rb". Scroll compressor. Any one of claims 1 to 5, wherein the rocking base plate portion of the rocking scroll is formed with an extraction hole for communicating the compression chamber and the second back pressure chamber during compression. Scroll compressor described in. The fixed frame is formed with an air extraction flow path that communicates the second oil flow path and the second back pressure chamber to introduce the oil in the second oil flow path into the second back pressure chamber. And
Claims 2 and 2 include a valve body that opens and closes the second oil flow path in the second oil flow path, and is provided with a pressure adjusting mechanism that adjusts the pressure in the second back pressure chamber. The scroll compressor according to any one of claims 3 to 6, which is subordinate to 2. 1. The scroll compressor according to any one of claims 7. A movable frame arranged between the swing scroll and the fixed frame is provided.
A third back pressure chamber in which the fluid of intermediate pressure is guided from the compression chamber during compression is formed between the movable frame and the fixed frame, and the movable is caused by the intermediate pressure in the third back pressure chamber. The scroll compressor according to any one of claims 1 to 8, wherein the frame floats and presses the swing scroll against the fixed scroll. The scroll compressor according to any one of claims 3 to 9, which is subordinate to claim 2 and claim 2, further comprising a pipe that connects the first oil flow path and the oil storage section.

Images