JP6570756B1 - Scroll compressor - Google Patents

Abstract

In the scroll compressor (1) according to the present invention, a compression chamber (RC) is formed between the fixed scroll (40) and the orbiting scroll (30) by the meshing of the orbiting wrap (32) and the fixed wrap (42). Has been. Further, the scroll compressor (1) opens and closes a bypass passage (71) that connects the compression chamber (RC) and a suction port (44) as a refrigerant supply unit that supplies gas refrigerant from the outside to the compression chamber (RC). A capacity control valve (62) is provided. The valve element (62a) included in the capacity control valve (62) communicates with a rear end side opening (62e) that opens to the rear end surface and a front end side opening (62f) that opens to the front side surface. A valve body hole (62ac) is provided. The valve body (62a) is in a state where the front end side opening portion (62f) is closed in a state where the valve body (62a) is positioned at the valve closing position, and the front end side opening portion is closed in a state where the bypass passage (71) is closed and is positioned in the valve opening position. (62f) is opened, and the bypass (71) is opened.

Description

  The present invention relates to a scroll compressor constituting a refrigeration cycle apparatus such as an air conditioner.

A scroll compressor is known as a compressor constituting a refrigeration cycle apparatus such as an air conditioner. And in a scroll compressor, in order to suppress the fall of the compression performance at the time of low load operation, the capacity control of the compression chamber is performed.
For example, in Patent Document 1, a bypass path (communication path) that leads from the inner line chamber side to the outer line chamber side of the compression chamber is provided, and a bypass valve (piston) that opens and closes the bypass path is provided.
During low load operation, the bypass valve is opened, and the refrigerant in the compression chamber is discharged from the extension chamber side to the outer line chamber side through the bypass passage, thereby reducing the substantial compression chamber capacity (low capacity operation). .
Further, during high load operation, the scroll compressor is operated with the bypass valve closed (high capacity operation).

JP 2007-154761 A

However, in Patent Document 1, in the bypass port section, when the orbiting wrap of the orbiting scroll (movable scroll) is shifted to one side, the extension side compression chamber and the outer line side compression chamber do not communicate with each other even if the bypass valve is opened. It has become.
For this reason, there is a problem that over compression is temporarily performed and pressure loss occurs.

  The present invention has been made in view of the above, and an object of the present invention is to provide a scroll compressor capable of performing capacity control while suppressing pressure loss due to overcompression.

In order to achieve the above object, a scroll compressor according to the present invention is formed on a fixed scroll having a spiral fixed wrap formed on one surface of a fixed end plate and on one side of a swivel end plate. A swirl scroll having a spiral shape and arranged between the fixed scroll and the orbiting scroll by meshing the orbiting scroll and the fixed wrap. A compression chamber, a refrigerant supply unit that supplies gas refrigerant to the compression chamber from the outside, a bypass path that communicates the compression chamber and the refrigerant supply unit, and a capacity control valve that opens and closes the bypass path; The valve body included in the capacity control valve includes a valve body hole that communicates a rear end side opening portion that opens to the rear end surface and a front end side opening portion that opens to the front end side surface, and a valve closing position. In the state of being located at the tip side opening There is closed to block the bypass passage, while located in the open position, the tip side opening is opened, the bypass port opened to the bypass passage, constituting the bypass passage, closed The valve body located at the position is formed by a through-hole penetrating the fixed end plate so that the valve body is located on the valve-opening side at a portion of the peripheral wall facing the distal end side opening of the valve body located at the valve-closed position. A port groove extending toward the surface is provided .

  ADVANTAGE OF THE INVENTION According to this invention, the scroll compressor which can perform capacity control can be provided, suppressing the pressure loss by overcompression.

It is sectional drawing which shows the compression mechanism which comprises the scroll compressor of 1st Embodiment. It is a perspective view which shows the valve body which comprises the capacity | capacitance control valve of 1st Embodiment. It is a principal part enlarged view which shows the state which the capacity | capacitance control valve in FIG. 1 opened. It is a principal part enlarged view which shows the state which the capacity | capacitance control valve in FIG. 1 closed. It is a perspective view which shows the valve body which comprises the capacity | capacitance control valve of 2nd Embodiment, and a bypass port. It is a principal part enlarged view which shows the state which the capacity | capacitance control valve in FIG. 1 opened. It is a principal part enlarged view which shows the state which the capacity | capacitance control valve in FIG. 1 closed. It is a perspective view which shows the valve body which comprises the capacity | capacitance control valve of 3rd Embodiment. It is a principal part enlarged view which shows the state which the capacity | capacitance control valve in FIG. 1 opened. It is a principal part enlarged view which shows the state which the capacity | capacitance control valve in FIG. 1 closed.

<First Embodiment>
A first embodiment of the present invention will be described in detail with reference to the drawings. In the description, the same elements are denoted by the same reference numerals, and redundant description is omitted.
A compression mechanism 2 constituting the scroll compressor 1 of the present invention is shown in FIGS.

The compression mechanism 2 is a structure for compressing the gas refrigerant introduced into the scroll compressor 1 to a high pressure, and is driven by an electric motor (not shown). The compression mechanism 2 includes a drive shaft 10, a scroll case 20, a turning scroll 30, a fixed scroll 40, an Oldham ring 50, and variable capacity means 60.
The drive shaft 10 also serves as an output shaft of the electric motor, and is supported so as to be rotatable around the shaft. Further, the drive shaft 10 includes an eccentric cam 11 at the tip thereof.
The eccentric cam 11 is composed of a columnar protrusion that is eccentrically projected from the axis of the drive shaft 10.

Next, the scroll case 20 will be described (see FIG. 1).
The outer shape of the scroll case 20 includes a cylindrical tube wall portion 21 and a bottom plate portion 22 that closes one end of the tube wall portion 21. Moreover, the outer peripheral flange part 43 of the fixed scroll 40 mentioned later is fastened to the cylinder wall part 21. As shown in FIG. The scroll case 20 forms a storage chamber RS together with the fixed scroll 40. Note that the orbiting scroll 30 and the Oldham ring 50 are accommodated in the accommodation chamber RS.
Further, the scroll case 20 includes a support portion 23.
The support part 23 is comprised by the bearing arrange | positioned in the center of the baseplate part 22, and is supporting the drive shaft 10 rotatably.

Next, the orbiting scroll 30 will be described (see FIG. 1).
The orbiting scroll 30 is accommodated in the accommodation chamber RS so as to be capable of turning. The orbiting scroll 30 includes an orbiting end plate 31, an orbiting wrap 32, and an orbiting bearing 33.
The swivel end plate 31 is formed of a disk-shaped member that can swivel inside the cylindrical wall portion 21 of the scroll case 20.
The orbiting wrap 32 is composed of a spiral wall protruding from the surface facing the fixed scroll 40.
The orbiting bearing 33 is configured by a round hole disposed at the center of the surface (the back surface of the orbiting wrap 32) facing the scroll case 20 of the orbiting end plate 31. And the eccentric cam 11 is inserted in the round hole of the turning bearing 33 so that rotation is possible, without backlash.

Next, the fixed scroll 40 will be described (see FIG. 1).
The fixed scroll 40 and the orbiting scroll 30 constitute a compression chamber RC. The fixed scroll 40 includes a fixed end plate 41, a fixed wrap 42, an outer peripheral flange portion 43, a suction port 44, and a discharge port 45.
The fixed end plate 41 is composed of a disk-shaped member having the same diameter as the bottom plate portion 22 of the scroll case 20.
The fixed wrap 42 is constituted by a spiral groove protruding from a surface facing the orbiting scroll 30. Further, the fixed wrap 42 meshes with the orbiting wrap 32 of the orbiting scroll 30, thereby forming an inner line side compression chamber on the inner line side of the orbiting wrap 32 and an outer line side compression chamber on the outer line side of the orbiting wrap 32.

The outer peripheral flange portion 43 is fastened by the cylindrical wall portion 21 of the scroll case 20 and a plurality of bolts (not shown), and the fixed scroll 40 is fixed to the scroll case 20.
The suction port 44 (refrigerant supply unit) is a supply port for supplying gas refrigerant from the outside to the compression chamber RC. The suction port 44 is configured by a through hole that opens to the groove bottom portion of the outer peripheral side groove end portion of the fixed wrap 42 and penetrates the fixed end plate 41.
The discharge port 45 is a discharge port for discharging the gas refrigerant compressed in the compression chamber RC to the outside. The discharge port 45 is formed by a through hole that opens to the groove bottom portion at the center of the fixed wrap 42 and penetrates the fixed end plate 41.

Next, the Oldham ring 50 will be described (see FIG. 1).
The Oldham ring 50 is formed of a substantially annular member, and is disposed between the scroll case 20 and the orbiting scroll 30 in the accommodation chamber RS. The Oldham ring 50 is displaced between the scroll case 20 and the orbiting scroll 30 in conjunction with the orbiting scroll 30, thereby restricting rotation when the orbiting scroll 30 is orbiting.

Next, the variable capacity means 60 will be described (see FIGS. 1 to 4).
The variable capacity means 60 is a structure for selectively switching the capacity of the compression chamber RC between a high capacity (high compression ratio) and a low capacity (low compression ratio). When the capacity is high, the entire volume of the compression chamber RC is used for compression of the gas refrigerant. When the capacity is low, a part of the volume of the compression chamber RC (on the discharge port 45 side) is compressed by the gas refrigerant. Used for.
The variable capacity means 60 includes a bypass port 61, a capacity control valve 62, and a control pipe 63.

As shown in FIGS. 3 and 4, the bypass port 61 is formed of a stepped through hole that penetrates the plate surface of the fixed end plate 41 and has holes having different diameters continuous in series. The bypass port 61 includes a small-diameter hole 61a, a large-diameter hole 61b, and a guide sleeve 61c.
The small-diameter hole portion 61 a constitutes a small-diameter portion of the stepped through hole, and is open to the groove bottom portion of the fixed wrap 42.

The large diameter hole portion 61b constitutes a large diameter portion of the stepped hole. The large-diameter hole 61b is a hole that opens in a plate surface (fixed wrap back surface) opposite to the fixed wrap 42 in the fixed end plate 41, and has a larger diameter than the small-diameter hole 61a.
The inner diameter of the large diameter hole 61b is set to the same size as the outer diameter of the front end of the guide sleeve 61c, and the guide sleeve 61c is inserted into the large diameter hole 61b.
In addition, the step part used as the boundary part of the small diameter hole part 61a and the large diameter hole part 61b is set to the port step part 61d.

The guide sleeve 61c is configured to guide the slide of a valve body 62a described later. The guide sleeve 61c is formed of a cylindrical body having a stepped outer shape whose front end is smaller in diameter than the rear end.
The front end of the guide sleeve 61c is inserted into the large-diameter hole 61b. The guide sleeve 61c has a rear end portion into which a collecting pipe 63c of a control pipe 63 described later is inserted.

Next, the capacity control valve 62 will be described (see FIGS. 1 to 4).
The capacity control valve 62 is configured to open and close the bypass port 61 and the bypass passage 71, and includes a valve body 62a and a valve spring 62b.
Note that the bypass passage 71 communicates the compression chamber RC and the suction port 44 (refrigerant supply portion) as a route for returning a part of the gas refrigerant in the compression chamber RC to the refrigerant supply portion side.
The valve body 62a has a stepped cylinder shape in which cylinders having different diameters are connected in series. Moreover, the valve body 62a is comprised by the large diameter columnar part 62aa and the small diameter columnar part 62ab, and the valve body hole 62ac has penetrated (refer FIG. 2).

The valve body 62a is slidably disposed in the bypass port 61 between the valve open position and the valve close position.
The valve opening position indicates a position where the valve element 62a is located when the capacity control valve 62 is opened, and the valve closing position is a position where the valve element 62a is located when the capacity control valve 62 is closed. Show.

The large-diameter columnar portion 62aa has a cylindrical shape and constitutes a rear end portion of the valve body 62a.
Further, the outer diameter of the large-diameter columnar portion 62aa is set to the same dimension as the inner diameter of the guide sleeve 61c.
That is, the guide sleeve 61c is set to a dimension that allows the large-diameter columnar portion 62aa to slide within the guide sleeve 61c without rattling.

The small-diameter columnar portion 62ab has a columnar shape that is smaller in diameter than the large-diameter columnar portion 62aa and is arranged on the same axis as the large-diameter columnar portion 62aa, and constitutes the front end portion of the valve body 62a.
In addition, the outer diameter of the small diameter columnar portion 62ab is set to the same size as the inner diameter of the small diameter hole portion 61a in the bypass port 61.
That is, the small diameter hole portion 61a is set to a size that allows the small diameter columnar portion 62ab to slide within the small diameter hole portion 61a without any gap.
In addition, the step part used as the boundary part of large diameter columnar part 62aa and small diameter columnar part 62ab is set to the valve body step part 62ad.

  The valve body hole 62ac is configured by a substantially T-shaped through hole that communicates the rear end surface of the large-diameter columnar portion 62aa and the side surface of the small-diameter columnar portion 62ab (see FIG. 2). An opening that opens to the rear end surface of the large-diameter columnar portion 62aa is referred to as a rear-end-side opening 62e, and an opening that opens to the side surface of the small-diameter columnar portion 62ab is referred to as a front-end-side opening 62f.

  The valve spring 62b is formed of a winding spring, and is nipped in a compressed state between the valve body step portion 62ad and the port step portion 61d while being wound around the small-diameter columnar portion 62ab. For this reason, the valve spring 62b urges the valve body 62a in the direction in which the valve opens by the repulsive force.

Next, the control piping 63 will be described (see FIG. 1).
The control pipe 63 is configured to selectively apply the suction pressure Ps or the storage chamber pressure Pb to the rear end surface of the valve body 62a through the gas refrigerant. The control pipe 63 includes a suction side pipe line 63a, a lubricating oil supply side pipe line 63b, a collecting pipe line 63c, and a three-way valve 63d.
One end of the suction side pipe 63a is connected to a suction port 44 (refrigerant supply unit) through which gas refrigerant is supplied to the scroll compressor 1 from the outside.

One end of the lubricating oil supply side pipe line 63b (intermediate pressure side pipe line) is connected to the storage chamber RS. The lubricant supply side pipe 63b is provided with a pressure reducing valve 63e as pressure adjusting means in the middle of the pipe.
The pressure reducing valve 63e (pressure adjusting means) is a structure for reducing the pressure in the storage chamber RS (storage chamber pressure Pb) to an appropriate pressure (intermediate pressure Pm).
The pressure after the pressure reduction by the pressure reducing valve 63e (intermediate pressure Pm) is set so that the following valve opening state and valve closing state are compatible with the spring constant of the valve spring 62b.

When the valve is opened, the suction pressure Ps is applied to the rear end surface (the rear end surface of the large-diameter columnar portion 62aa) of the valve body 62a. However, as shown in FIG. 4, the valve spring 62b biases and holds the valve body 62a at the valve opening position against the suction pressure Ps and opens the small-diameter hole 61a of the bypass port 61 (valve open state). .
When the valve is closed, the pressure (intermediate pressure Pm) adjusted by the pressure reducing valve 63e is applied to the rear end face side of the valve body 62a. As shown in FIG. 3, the valve spring 62b is compressed by the intermediate pressure Pm, the valve body 62a moves to the valve closing position, and closes the small diameter hole 61a of the bypass port 61 (valve closed state).
Since the pressure reducing valve 63e is a commonly used configuration, a detailed description of the configuration is omitted.

One end of the collecting pipe 63c is connected to the guide sleeve 61c.
The other ends of the suction side pipe line 63a, the lubricating oil supply side pipe line 63b, and the collecting pipe line 63c are connected to the three-way valve 63d.
By operating the three-way valve 63d, the communication between the suction port 44 and the guide sleeve 61c and the communication between the storage chamber RS and the guide sleeve 61c are selectively switched.
Then, by the switching operation of the three-way valve 63d, the pressure applied to the rear end surface of the valve body 62a is switched to the suction pressure Ps or the intermediate pressure Pm.

Next, the function of the variable capacitance means 60 will be described.
<When the scroll compressor 1 is used with a high capacity (high compression ratio) (see FIGS. 1 and 3)>
The three-way valve 63d is operated to connect the lubricating oil supply side pipe line 63b and the collecting pipe line 63c, and an intermediate pressure Pm is applied to the rear end of the valve body 62a through the gas refrigerant. When the intermediate pressure Pm is applied to the rear end surface of the valve body 62a, the valve spring 62b is compressed and the valve body 62a moves to the valve closing position.
In the valve body 62a at the valve closing position, the front end portion (small-diameter columnar portion 62ab) of the valve body 62a is inserted into the bypass port 61, and the front end surface of the small-diameter columnar portion 62ab contacts the turning wrap 32.
That is, when the valve is closed, the front end surface is located on the same plane as the groove bottom portion of the fixed wrap 42.

In this state, the valve body 62 a closes the small diameter hole 61 a of the bypass port 61. As the small diameter columnar portion 62ab is inserted into the small diameter hole portion 61a, the peripheral wall of the small diameter hole portion 61a closes the distal end side opening portion 62f of the valve body 62a.
As a result, the bypass path 71 is blocked.
In addition, since the applied intermediate pressure Pm is higher than the pressure in the compression chamber RC immediately after the start of compression, the finely divided lubricating oil mixed in the gas refrigerant travels along the wall of the control pipe 63 and the valve body 62a. It enters the gap with the bypass port 61.

Thereby, the airtightness of the capacity control valve 62 when the valve is closed is enhanced.
That is, the storage chamber RS functions as a lubricating oil supply unit, and the lubricating oil is supplied to the capacity control valve 62 through the control pipe 63.
In a state where the capacity control valve 62 blocks the bypass port 61, the entire volume of the compression chamber RC is used for compression, and the compression ratio becomes a high compression ratio.
The case where the scroll compressor 1 is operated in this state is referred to as high load operation (high capacity operation).

<When the scroll compressor 1 is used at a low capacity (low compression ratio) (see FIGS. 1 and 4)>
The three-way valve 63d is operated to connect the suction side pipe line 63a and the collecting pipe line 63c, and the suction pressure Ps is applied to the rear end of the valve body 62a through the gas refrigerant.
By applying the suction pressure Ps to the rear end surface of the valve body 62a, the repulsive force of the valve spring 62b resists the suction pressure Ps and moves the valve body 62a to the valve opening position.
The valve body 62a at the valve opening position has the rear end portion of the valve body 62a butted against the front end of the guide sleeve 61c while the front end portion of the valve body 62a is disengaged from the small diameter hole portion 61a of the bypass port 61.

In this state, the compression chamber RC and the large diameter hole 61b of the bypass port 61 communicate with each other. As the front end portion of the valve body 62a is separated from the small diameter hole portion 61a, the front end side opening 62f of the valve body hole 62ac that is closed by the peripheral wall of the small diameter hole portion 61a opens.
As a result, the small-diameter hole 61a, the large-diameter hole 61b, the valve element hole 62ac, the collecting pipe 63c, and the suction-side pipe 63a are communicated in this order to bypass the compression chamber RC and the suction port 44 (refrigerant supply part). The bypass path 71 is opened.

When the bypass passage 71 is opened, the gas refrigerant supplied from the suction port 44 to the compression chamber RC is discharged from the bypass port 61 to the suction port 44 without being compressed. Then, the gas refrigerant is compressed with the volume from the bypass port 61 to the discharge port 45 in the compression chamber RC.
In a state where the capacity control valve 62 opens the bypass port 61, a part of the volume of the compression chamber RC is used for compression, and the compression ratio becomes a low compression ratio.
The case where the scroll compressor 1 is operated in this state is referred to as low load operation (low capacity operation).

Next, the effect of the scroll compressor 1 according to the present embodiment will be described.
The valve body 62a constituting the capacity control valve 62 of the present embodiment includes a valve body hole 62ac that communicates the rear end side opening 62e that opens to the rear end face and the front end side opening 62f that opens to the side face of the front end. ing. The valve body hole 62ac constitutes a part of the bypass passage 71.
Further, it is set so that the distal end side opening 62f is closed and the bypass passage 71 is closed in a state where the valve body 62a is located at the valve closing position.

And it sets so that the front end side opening part 62f may be open | released and the bypass path 71 may be opened in the state which the valve body 62a was located in the valve opening position.
By adopting such a configuration, gas refrigerant is supplied and discharged from the bypass port 61 into the compression chamber RC in addition to the suction port 44 (refrigerant supply unit) during capacity control (low capacity operation). Can do.
As a result, the refrigerant can be bypassed regardless of the rotation angle of the orbiting scroll 30, so that the capacity control operation (low capacity operation) can be performed while suppressing the pressure loss due to overcompression.

In this embodiment, with the capacity control valve 62 closed, the lubricating oil supply side pipe 63b (intermediate pressure side pipe) and the collecting pipe 63c communicate with each other through the three-way valve 63d (switching means). 72 is formed. An oil film is formed in the gap between the valve body 62 a and the bypass port 61 by the lubricating oil mixed in the gas refrigerant supplied from the storage chamber RS to the capacity control valve 62 through the lubricating oil passage 72.
By forming an oil film in the gap between the valve element 62a and the bypass port 61, the airtightness of the capacity control valve 62 is increased and the leakage of the refrigerant when the valve is closed is suppressed. Can be increased.
Further, since the lubricating oil oozes out from the gap into the compression chamber RC, lubrication between the tip of the orbiting wrap 32 and the fixed scroll 40 can be performed.

In the capacity control valve 62 of the present embodiment, the valve body 62a is opposed to the spring force of the valve spring 62b by the pressure applied to the rear end surface of the valve body 62a when the valve is closed, and the tip of the valve body 62a is in the compression chamber RC. It is urged to protrude.
With such a configuration, the distal end surface of the valve body 62a abuts on the turning lap 32 when the valve is closed (during high capacity operation).
As a result, the space where the refrigerant cannot be compressed in the bypass port 61 and refrigerant leakage are reduced, and the compression efficiency during high capacity operation can be increased.

In the present embodiment, a pressure reducing valve 63e (pressure adjusting means) is provided in a lubricating oil supply side pipe 63b (intermediate pressure side pipe) located between the storage chamber RS (lubricating oil supply part) and the capacity control valve 62. Is arranged.
The pressure reducing valve 63e is arranged to adjust the pressure of the gas refrigerant supplied from the storage chamber RS.
For example, when the pressure of the valve body 62a is excessively strong to push the turning wrap 32 when the pressure is supplied in the accommodation chamber RS, the turning wrap 32 may be detached from the fixed scroll 40.

As a countermeasure, when the force for pressing the orbiting scroll 30 against the fixed scroll 40 is increased, the frictional resistance with the fixed scroll 40 when the orbiting scroll 30 revolves increases, and the driving efficiency decreases.
Therefore, a pressure reducing valve 63e is disposed in order to adjust the force pressing the orbiting scroll 30 against the fixed scroll 40 to an appropriate strength.
Thereby, the compression efficiency can be increased while suppressing a decrease in the operation efficiency during the high capacity operation.

In the present embodiment, the spring constant of the valve spring 62b is such that the load applied to the valve body 62a by the gas refrigerant when the valve is closed resists the spring force of the valve spring 62b, thereby moving the valve body 62a from the valve opening position to the valve closing position. It is set to be movable.
With such a setting, when closing the capacity control valve 62, the valve body 62a can be reliably moved to the valve closing position.
As a result, the capacity control valve 62 is not closed, and the gas refrigerant can be prevented from coming out of the cylinder and flowing into the compression chamber RC.

<Second Embodiment>
Next, a second embodiment of the scroll compressor 1 will be described with reference to FIGS. The same components as those of the scroll compressor 1 described above are denoted by the same reference numerals, and redundant description is omitted.
As shown in FIGS. 5 to 7, the configuration greatly different from the first embodiment is the shape of the bypass port 61 of the variable capacity means 60.
A port groove 61e is provided on the peripheral wall of the small-diameter hole 61a constituting the bypass port 61.
The port groove 61e has a substantially rectangular cross section at a portion facing the distal end side opening 62f of the valve body 62a located at the valve closing position on the peripheral wall of the small diameter hole 61a, and extends toward the valve opening side. (See FIG. 5).

Next, the function of the variable capacitance means 60 will be described.
<When the scroll compressor 1 is used with a high capacity (high compression ratio) (see FIG. 6)>
The valve body 62a is located at the valve closing position as in the first embodiment.
In this state, in the valve body 62a, the small diameter columnar portion 62ab is inserted into the small diameter hole portion 61a, and the small diameter hole portion 61a of the bypass port 61 is closed.

<When the scroll compressor 1 is used with a low capacity (low compression ratio) (see FIG. 7)>
In the state where the valve body 62a is located at the valve opening position, the tip of the small-diameter columnar portion 62ab remains in the small-diameter hole portion 61a, but the small-diameter hole portion 61a and the large-diameter hole portion 61b pass through the port groove 61e. Communicate.
As a result, the small-diameter hole portion 61a, the port groove 61e, the valve body hole 62ac, the collecting duct 63c, and the suction-side duct 63a are communicated in this order, and the bypass path 71 that bypasses the compression chamber RC and the suction port 44 is opened. (See FIG. 1).

Next, the effect of the scroll compressor 1 according to the present embodiment will be described.
In the valve body 62a of the first embodiment, the small-diameter columnar portion 62ab is detached from the small-diameter hole portion 61a at the valve opening position.
For this reason, when the valve body 62a moves from the valve opening position to the valve closing position, there is a possibility that a phenomenon in which the small diameter columnar portion 62ab does not easily enter the small diameter hole portion 61a may occur due to dimensional accuracy, thermal expansion due to temperature change, and the like. is there.
However, in the present embodiment, the bypass path 71 can be opened while the tip end portion of the small diameter columnar portion 62ab is left in the small diameter hole portion 61a.
Thereby, the valve body 62a can be moved more reliably from the valve opening position to the valve closing position.

<Third Embodiment>
Next, a third embodiment of the scroll compressor 1 will be described with reference to FIGS. The same components as those of the scroll compressor 1 described above are denoted by the same reference numerals, and redundant description is omitted.
As shown in FIGS. 8 to 10, the configuration greatly different from the first embodiment described above is the shape of the valve body hole 62ac that opens to the valve body 62a that constitutes the capacity control valve 62, and the shape of the guide sleeve 61c. .
The valve element hole 62ac is configured by a substantially T-shaped through hole that communicates the rear end surface of the large-diameter columnar portion 62aa and the side surface of the large-diameter columnar portion 62aa (see FIG. 8).
And the opening part opened to the rear-end surface of a large diameter columnar part is called the rear end side opening part 62e, and the opening part opened to the side surface of a large diameter columnar part is called the front end side opening part 62f.
The guide sleeve 61c has an inner diameter on the distal end side that is larger than a portion facing the distal opening 62f in a state where the valve body 62a is positioned at the valve opening position (sleeve expanded portion 61f).

Next, the function of the variable capacitance means 60 will be described.
<When the scroll compressor 1 is used at a high capacity (high compression ratio) (see FIG. 9)>
The valve body 62a is located at the valve closing position as in the first embodiment.
In this state, in the valve body 62a, the small diameter columnar portion 62ab is inserted into the small diameter hole portion 61a, and the small diameter hole portion 61a of the bypass port 61 is closed.

<When the scroll compressor 1 is used with a low capacity (low compression ratio) (see FIG. 10)>
In the state where the valve body 62a is located at the valve closing position, the small-diameter columnar portion 62ab is detached from the small-diameter hole portion 61a, and the valve-body step portion 62ad is moved to the sleeve enlarged-diameter portion 61f. The sleeve enlarged diameter portion 61f communicates (see FIG. 1).
Accordingly, the compression chamber RC and the suction port 44 (refrigerant) are communicated in the order of the small diameter hole portion 61a, the large diameter hole portion 61b, the sleeve enlarged diameter portion 61f, the valve body hole 62ac, the collecting duct 63c, and the suction side duct 63a. A bypass path 71 that bypasses the supply section is opened.

Next, the effect of the scroll compressor 1 according to the present embodiment will be described.
In the valve body 62a of the present embodiment, the valve body hole 62ac is configured by a substantially T-shaped through hole that communicates the rear end surface of the large-diameter columnar portion 62aa and the side surface of the large-diameter columnar portion 62aa. The same effects as those of the first embodiment can be obtained.

DESCRIPTION OF SYMBOLS 1 Scroll compressor 30 Orbiting scroll 31 Orbiting end plate 32 Orbiting wrap 40 Fixed scroll 41 Fixed end plate 42 Fixed wrap 44 Suction port (refrigerant supply part)
61 Bypass port 61e Port groove 62 Capacity control valve 62a Valve body 62ac Valve body hole 62b Valve spring 62e Rear end side opening 62f Front end side opening 63a Suction side pipe 63b Lubricating oil supply side pipe (intermediate pressure side pipe)
63c Collecting pipe line 63d Three-way valve (switching means)
63e Pressure reducing valve (pressure adjusting means)
71 Bypass path 72 Lubricating oil path RC Compression chamber RS Storage chamber (lubricating oil supply part)

Claims (5)

A fixed scroll having a spiral fixed wrap formed on one surface of the fixed endplate;
A orbiting scroll having a spiral orbiting lap formed on one surface of the orbiting end plate, and arranged to be orbitable with respect to the fixed scroll;
A compression chamber formed between the fixed scroll and the orbiting scroll by meshing the orbiting wrap and the fixed wrap;
A refrigerant supply unit for supplying gas refrigerant to the compression chamber from the outside;
A bypass passage communicating the compression chamber and the refrigerant supply unit;
A capacity control valve for opening and closing the bypass path;
With
The valve body included in the capacity control valve is:
A rear end opening that opens to the rear end surface;
A tip side opening that opens to the tip side surface;
It has a valve body hole that communicates,
In the state of being in the valve closing position, the opening on the distal end side is closed to block the bypass path,
In the state of being located at the valve opening position, the distal end side opening is opened, and the bypass passage is opened ,
The bypass port constituting the bypass path is
The valve body located at the valve closing position can be inserted,
It consists of a through-hole that penetrates the fixed end plate,
A scroll compressor characterized in that a port groove extending toward the valve opening side is provided at a portion of the peripheral wall facing the tip side opening of the valve body located at the valve closing position . A suction-side pipe line having one end communicating with the refrigerant supply unit;
An intermediate pressure side conduit having one end communicating with the lubricating oil supply section;
A collecting pipe having one end communicating with the capacity control valve;
The other ends of the suction side pipe, the intermediate pressure side pipe, and the collecting pipe are connected via switching means,
Through the switching means, the suction side pipe line and the collecting pipe line communicate with each other to form the bypass path,
2. The scroll compressor according to claim 1, wherein a lubricating oil passage is formed by communicating the intermediate pressure side pipe line and the collecting pipe line through the switching unit. The valve body is
2. The scroll compressor according to claim 1, wherein, when the valve is closed, a front end surface thereof is urged so as to come into contact with the swing wrap. The scroll compressor according to claim 2, further comprising a pressure adjusting unit in the intermediate pressure side pipe line. A valve spring for biasing the valve body from the valve closing position side toward the valve opening position side;
The spring constant of the valve spring is
When the intermediate pressure side pipe line and the collecting pipe line communicate with each other, a load applied to the valve body by the gas refrigerant supplied from the lubricating oil supply unit resists the spring force of the valve spring, and the valve The scroll compressor according to claim 2, wherein the body is set to be movable from the valve opening position to the valve closing position.

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