JP5360709B2 - Hermetic compressor and refrigeration cycle equipment - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a hermetic compressor variable in capacity between full capacity operation and half capacity operation, simplifying a constitution, reducing man-hours by decreasing the number of parts, suppressing influences on cost and shortening a time for switching operation, and to provide a refrigerating cycle apparatus equipped with the hermetic compressor. <P>SOLUTION: At least a portion of a pressure switching valve K is built in a sealed container 1 for switching the pressure of a second blade chamber 10b formed in a second cylinder 6B between discharge pressure and suction pressure. The pressure switching valve has a valve body 21 having a slider hole 25 along the axial direction, and a slider 24 arranged in the slider hole. The slider can be switched between a first operation position at which the second blade chamber and a space in the sealed container communicate with each other and a second operation position at which the second blade chamber and a suction communication passage 26 connected with a second cylinder chamber communicate with each other. <P>COPYRIGHT: (C)2010,JPO&amp;INPIT

Description

  The present invention relates to a hermetic compressor capable of switching a compression capacity, and a refrigeration cycle apparatus including the hermetic compressor and constituting a refrigeration cycle.

  A hermetic compressor having a cylinder chamber in each of the first cylinder constituting the first compression mechanism and the second cylinder constituting the second compression mechanism is often used. In this type of compressor, it is advantageous if a so-called variable capacity can be achieved in which the compression action is performed simultaneously in two cylinder chambers or the compression action in one of the cylinder chambers is interrupted to reduce the compression work.

  For example, [Patent Document 1] provides a branch pipe that branches from a suction pipe that communicates an accumulator and a second cylinder chamber, communicates with a blade chamber provided in the branch pipe and the second cylinder, and includes a sealed container. An invention is disclosed that includes a piping configuration that communicates with the inner bottom of the pipe, includes a first on-off valve in the branch pipe, and a second on-off valve in the pipe that communicates with the inner bottom of the sealed container.

  When the first on-off valve is closed and the second on-off valve is opened, the discharge pressure (lubricating oil) in the sealed container is guided to the blade chamber, and a high back pressure is applied to the blade in the cylinder chamber. Make compression work. In the other cylinder chamber, a normal compressing action is performed, and the compressing action is simultaneously performed in the two chambers, resulting in full capacity operation.

  When the first on-off valve is opened and the second on-off valve is closed, the suction pressure (low pressure gas refrigerant) derived from the accumulator is guided to the blade chamber. A low pressure back pressure is applied to the blade, and a low pressure atmosphere having the same pressure as the cylinder chamber is created. In this cylinder chamber, no compression action is performed, and only the other cylinder chamber is compressed, resulting in a half capacity operation.

[Patent Document 2] discloses an invention in which a blade chamber is partitioned by a cylinder and an airtight container, and a slider is reciprocated by an electromagnetic coil to open and close a suction passage that connects the suction pipe and the blade chamber.
When the slider is moved to open the suction passage and the blade chamber communicates with the suction pipe, the blade chamber becomes low pressure. The blade is pulled by a spring member, and compression action is not performed in one cylinder chamber, but compression operation is performed in the other cylinder chamber.

  When the slider is moved in the reverse direction and the suction passage is closed, a gas having a discharge pressure is introduced into the blade chamber from between the cylinder and the sealed container. The blade chamber has a high pressure, and the blade is pressed and urged to compress in the cylinder chamber. The other cylinder chamber performs a normal compression action, and the two chambers are operated simultaneously.

JP 2006-300460 A JP-A-5-256286

  However, in [Patent Document 1], a branch pipe branched from the suction pipe, a pipe communicating with the inner bottom of the sealed container, a pipe communicating with the blade chamber, and two on-off valves must be prepared. In addition, a member for partitioning the blade chamber into a closed space is also necessary, and the number of parts increases and the part cost increases.

  Naturally, a lot of man-hours are required for mounting and assembling each component, which has an adverse effect on cost. Furthermore, since piping parts and on-off valves are attached to the outside of the hermetic container, a large space is required for installing the compressor, and it is difficult to install a soundproof material.

  In [Patent Document 2], since the discharge gas is configured to be guided to the blade chamber through a gap between the cylinder and the hermetic container, it takes time until the pressure of the blade chamber is increased. Therefore, there is a delay in switching from the compression pause of the second cylinder chamber to the compression action. If the gap is increased, the amount of discharge gas leaking to the suction side during compression stop increases, resulting in a reduction in efficiency.

  The cylinder shape is special and it is difficult to standardize with a cylinder that always performs compression operation. If the slider and cylinder are not precisely aligned, the suction communication path cannot be blocked by the slider. The configuration in which the blade chamber is partitioned by the cylinder and the sealed container is difficult in terms of processing. Lubricating oil is not supplied to the blade chamber during the compression operation, and the sliding between the blade and the cylinder tends to be hindered.

  The present invention has been made on the basis of the above circumstances, and the object thereof is a two-cylinder type, and on the premise that the compression capacity can be changed, the structure is simplified and the number of parts is reduced. A hermetic compressor that can reduce costs and reduce the time required for operation switching, and a refrigeration system that can improve the refrigeration cycle efficiency with this hermetic compressor A cycle device is to be provided.

In order to satisfy the above object, a hermetic compressor according to the present invention accommodates an electric motor part and a compression mechanism part in a hermetic container, and the compression mechanism part includes a first cylinder and a second cylinder with an intermediate partition plate interposed therebetween. A cylinder chamber was formed in each inner diameter portion, and a blade chamber communicating with each cylinder chamber was provided.
A first eccentric part and a second eccentric part are provided on a rotating shaft connected to the electric motor part, and these are accommodated in the first cylinder chamber and the second cylinder chamber, respectively. The first eccentric roller and the second eccentric roller are fitted to the two eccentric portions, and are driven to rotate in the first cylinder chamber and the second cylinder chamber.
The first blade chamber and the second blade chamber are movably accommodated in the first blade chamber and the second blade chamber, and are brought into contact with the first eccentric roller and the second eccentric roller, respectively. A cylinder chamber and a second cylinder chamber are partitioned.
Only the first cylinder is provided with a spring member for applying an elastic force to the first blade. The second blade is pressed and urged to come into contact with the second eccentric roller by the discharge pressure guided to the second blade chamber, and is held away from the second eccentric roller by the suction pressure guided to the second blade chamber.
At least a part of a pressure switching valve for switching the pressure of the second blade chamber between the discharge pressure and the suction pressure is built in the sealed container, and the pressure switching valve has a valve body having a slider hole, and the valve body. And a slider disposed in the slider hole.
A blade chamber communication passage communicating with the second blade chamber, a suction communication passage communicating with the suction side of the second cylinder chamber, and a discharge communication passage communicating with the inside of the sealed container are connected to the slider hole of the pressure switching valve. To do. A notch is provided in a part of the peripheral surface of the slider so that the suction communication path or the discharge communication path communicates with the blade chamber communication path according to the position of the slider.
The slider has a first operation position that communicates the second blade chamber and the space in the sealed container, and a second operation position that communicates the second blade chamber and the suction side of the second cylinder chamber. Switching is possible.

  According to the present invention, on the assumption that the compression capacity is variable with a two-cylinder type, the structure is simplified and the number of parts is reduced to reduce the number of man-hours. It is possible to provide a hermetic compressor that can shorten the time required for operation switching, and a refrigeration cycle apparatus that includes this hermetic compressor and can improve refrigeration cycle efficiency.

The longitudinal cross-sectional view which a part of the hermetic compressor provided with the pressure switching valve concerning a 1st embodiment in the present invention omitted, and the refrigeration cycle block diagram of the refrigerating cycle device. The cross-sectional plan view of the hermetic compressor according to the first embodiment. The front view of the pressure switching valve based on the said 1st Embodiment, and the top view of a mutually different state of a pressure switching valve. Sectional drawing which abbreviate | omitted one part of the hermetic compressor provided with the pressure switching valve based on 2nd Embodiment in this invention. The expanded longitudinal cross-sectional view of the principal part of the hermetic type compressor which shows the state at the time of full capacity operation based on the said 2nd Embodiment. The expanded longitudinal cross-sectional view of the principal part of the hermetic type compressor which shows the state at the time of a half capacity | capacitance driving based on the said 2nd Embodiment. The cross-sectional top view of the principal part of a hermetic compressor based on 3rd Embodiment in this invention. The longitudinal cross-sectional view of the principal part of a hermetic type compressor based on 4th Embodiment in this invention. The top view and longitudinal cross-sectional view which followed the BB line of the pressure switching valve based on 5th Embodiment in this invention. The longitudinal cross-sectional view of the principal part of the hermetic compressor which shows the state of the pressure switching valve at the time of full capacity driving | operation and half capacity driving | operation based on 6th Embodiment in this invention. The longitudinal cross-sectional view of the principal part of the sealed compressor which shows the state of the pressure switching valve at the time of full capacity driving | operation based on the modification in 6th Embodiment. The longitudinal cross-sectional view of the principal part of the sealed compressor which shows the state of the pressure switching valve at the time of full capacity driving | operation based on the further different modification in 6th Embodiment. The longitudinal cross-sectional view and transverse cross-sectional view of the principal part of a hermetic compressor which show the state of the pressure change-over valve at the time of half capacity operation according to a 7th embodiment in the present invention. The longitudinal cross-sectional view and cross-sectional plan view of the principal part of a hermetic type compressor which show the state of the pressure switching valve at the time of full capacity operation based on the said 7th Embodiment. The longitudinal cross-sectional view of the principal part of the hermetic type compressor which shows the state of the pressure switching valve at the time of a half capacity | capacitance operation based on the modification in the said 7th Embodiment. The top view of a part of cylinder which shows the attachment structure of the permanent magnet based on 8th Embodiment in this invention. The top view of the cylinder part which shows the attachment structure by the 1st holding member which hold | maintains a permanent magnet based on the modification in the 8th Embodiment, and the top view of a 2nd holding member. The perspective view, front view, and side view of a 1st holding member which concern on the modification in the said 8th Embodiment.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.
FIG. 1 is a diagram illustrating a cross-sectional structure in which a part of the hermetic compressor R is omitted and a refrigeration cycle configuration of a refrigeration cycle apparatus including the hermetic compressor R. (In order to avoid complications in the drawings, there are parts that are not labeled even if they are described. The same applies hereinafter.)
First, the hermetic compressor R will be described. Reference numeral 1 denotes a hermetic container, and a lower part in the hermetic container 1 is provided with a first compression mechanism part 3A and a second compression mechanism part 3B via an intermediate partition plate 2. Is provided, and an electric motor unit 4 is provided at the top. The first compression mechanism unit 3 </ b> A and the second compression mechanism unit 3 </ b> B are connected to the electric motor unit 4 by the rotation shaft 5.

  The first compression mechanism portion 3A includes a first cylinder 6A, and the second compression mechanism portion 3B includes a second cylinder 6B. The main bearing 7 is attached and fixed to the upper surface portion of the first cylinder 6A, and the auxiliary bearing 8 is attached and fixed to the lower surface portion of the second cylinder 6B. The rotating shaft 5 integrally includes a first eccentric portion a and a second eccentric portion b formed with a phase difference of about 180 ° while penetrating through the cylinders 6A and 6B.

  The eccentric parts a and b have the same diameter as each other, and are assembled so as to be positioned at the inner diameter parts of the cylinders 6A and 6B. A first eccentric roller 9a is fitted to the peripheral surface of the first eccentric part a, and a second eccentric roller 9b is fitted to the peripheral surface of the second eccentric part b.

  A first cylinder chamber Sa is formed in the inner diameter portion of the first cylinder 6A, and a second cylinder chamber Sb is formed in the inner diameter portion of the second cylinder 6B. The cylinder chambers Sa and Sb are formed to have the same diameter and height, and a part of the peripheral wall of the eccentric rollers 9a and 9b is accommodated so as to be eccentrically rotatable while making line contact with a part of the peripheral wall of the cylinder chambers Sa and Sb. The

  The first cylinder 6A is provided with a first blade chamber 10a communicating with the first cylinder chamber Sa, and the first blade 11a is movably accommodated therein. The second cylinder 6B is provided with a second blade chamber 10b communicating with the second cylinder chamber Sb, and the second blade 11b is movably accommodated therein.

  The tip portions of the first and second blades 11a and 11b are formed in a semicircular shape in a plan view, and project into the opposing cylinder chambers Sa and Sb so as to have a circular shape in a plan view. Line contact can be made with the peripheral walls of the rollers 9a and 9b regardless of the rotation angle.

  Only the first cylinder 6A is provided with a lateral hole that communicates the first blade chamber 10a with the outer peripheral surface of the cylinder 6A, and accommodates a spring member 14 that is a compression spring. The spring member 14 is interposed between the rear end face of the first blade 11a and the inner peripheral wall of the sealed container 1, and applies an elastic force (back pressure) to the blade 11a.

  The second blade chamber 10b provided in the second cylinder 6B is provided with a second blade 11b and a pressure switching valve K described later. A discharge pressure (high pressure) or suction pressure (low pressure) back pressure can be applied to the blade 11b in accordance with the switching operation of the pressure switching valve K, and the leading edge can be brought into contact with or separated from the eccentric roller 9b.

  An oil reservoir 15 for collecting lubricating oil is formed at the inner bottom of the sealed container 1. In FIG. 1, the broken line crossing the flange portion of the main bearing 7 indicates the level of the lubricating oil, and almost all of the first compression mechanism portion 3A and all of the second compression mechanism portion 3B It is immersed in the lubricating oil of the reservoir 15.

  This is a hermetic compressor R configured as described above, and a discharge pipe P is connected to the upper end of the hermetic container 1. The discharge pipe P is connected to the upper end portion of the accumulator 20 via the condenser 17, the expansion device 18 and the evaporator 19. The accumulator 20 and the hermetic compressor R are connected via a first suction pipe Pa and a second suction pipe Pb.

  The first suction pipe Pa penetrates the sealed container 1 constituting the hermetic compressor R and the side of the first cylinder 6A and communicates with the first cylinder chamber Sa. The second suction pipe Pb penetrates the sealed container 1 and the side of the second cylinder 6B and communicates with the second cylinder chamber Sb.

The refrigeration cycle apparatus is configured by sequentially connecting the hermetic compressor R, the condenser 17, the expansion device 18, the evaporator 19, and the accumulator 20 as described above.
Next, the pressure switching valve K will be described in detail.

  FIG. 2 is a cross-sectional plan view of the hermetic compressor R provided with the pressure switching valve K in the first embodiment. FIG. 3A is a schematic front view of the pressure switching valve K. FIG. 3 (B) and 3 (C) are schematic plan views of the pressure switching valve K in different states.

  The pressure switching valve K is immersed in the lubricating oil in the oil reservoir 15 formed at the inner bottom of the sealed container 1, and the valve main body 21, the electromagnetic coil 22, and the magnetic member 23 are integrally connected. And a slider 24.

  In the plan view shown in FIGS. 2 and 3B and 3C, the valve body 21 is curved at the inner side and the outer side, and in the front view shown in FIG. It has a substantially prismatic shape formed in a flat shape. A slider hole 25 having a perfectly circular cross section is provided through the left and right end surfaces of the valve body 21.

  A suction communication passage 26 formed of a hole, a blade chamber communication passage 27 and a discharge communication passage 28 are provided at a predetermined distance from one end face of the valve body 21 so as to be separated from each other and arranged side by side. Each of the communication passages 26 to 28 is provided from the outer peripheral surface of the valve body 21 to the slider hole 25, and communicates the outside of the valve body 21 and the slider hole 25.

  The suction communication path 26 and the blade chamber communication path 27 are opened on the same side surface of the valve body 21, and the discharge communication path 28 is opened on the side surface of the valve body 21 opposite to the suction communication path 26 and the blade chamber communication path 27. Is done.

The distance from the suction communication passage 26 and the distance from the discharge communication passage 28 are set to be the same with respect to the blade chamber communication passage 27. The diameters of the blade chamber communication path 27 and the discharge communication path 28 are set to be the same, and the suction communication path 26 is formed to have a smaller diameter than these diameters.
The electromagnetic coil 22 is integrally connected to the end surface of the valve body 21 on the side where the discharge communication passage 28 is provided, and has an inner peripheral portion 29 having substantially the same diameter as the slider hole 25.

  The slider 24 has a cylindrical shape that is slidably fitted over a slider hole 25 provided in the valve main body 21 and an inner peripheral portion 29 of the electromagnetic coil 22. A cutout portion 30 having a further reduced outer diameter is provided at a substantially intermediate portion along the axial direction on the peripheral surface of the slider 24.

  The magnetic member 23 is connected to or integrally formed with one end face of the slider 24, and is shown only in FIG. 3C and omitted in FIG. 3B. The outer diameter of the magnetic member 23 is formed to be the same as the outer diameter of the slider 24. A compression spring (not shown) abuts on the end surface opposite to the slider 24, and the magnetic member 23 and the slider 24 are elastic along the axial direction. Is urged to press.

  Thus, when the electromagnetic coil 22 is energized and the magnetic member 23 is magnetically attracted against the elastic force of the compression spring, the slider 24 has the notch 30 as shown in FIG. It is displaced to a position facing the communication passage 27 and the discharge communication passage 28. The position of the slider 24 at this time is referred to as a “first operation position”.

  When the electromagnetic coil 22 is disconnected, the magnetic attractive action on the magnetic member 23 is lost. Instead, the elastic force of the compression spring acts, and the slider 24 is displaced to a position where the notch portion 30 faces the blade chamber communication passage 27 and the suction communication passage 26 as shown in FIG. The position of the slider 24 at this time is referred to as a “second operation position”.

  As shown in FIG. 1 again, the pressure switching valve K is attached to the lower surface of the second cylinder 6B and closes the lower open surface of the second blade chamber 10b. The upper open surface of the second blade chamber 10b is closed by the intermediate partition plate 2 interposed between the first cylinder 6A and the second cylinder 6B, and the upper surface of the second blade chamber 10b is The lower surface is in a closed state.

The second cylinder 6B is provided with a suction hole to which the second suction pipe Pb is connected and a communication hole that communicates the lower surface of the second cylinder 6B. As schematically shown in FIG. 2, the suction communication passage 26 provided in the valve body 21 at the pressure switching valve K is configured to communicate with the second suction pipe Pb through the communication hole. .
The blade chamber communication passage 27 is opened to the second blade chamber 10 b, and the discharge communication passage 28 is opened to the oil reservoir 15 in the sealed container 1.

  In the hermetic compressor R including the pressure switching valve K as described above and the refrigeration cycle apparatus equipped with the hermetic compressor R, the operation of the pressure switching valve K causes normal operation (full capacity operation), Switching to cylinder operation (half-capacity operation) can be selected.

  When the normal operation is selected, the electromagnetic coil 22 of the pressure switching valve K is energized, and the magnetic member 23 and the slider 24 are magnetically attracted against the elastic force of the compression spring. The slider 24 is moved and displaced to the first operating position shown in FIG. 3B, and the blade chamber communication passage 27 and the discharge communication passage 28 are communicated with the notch 30. Therefore, the second blade chamber 10b and the oil reservoir 15 are communicated with each other via the pressure switching valve K.

  An operation signal is sent to the motor unit 4 and the rotary shaft 5 is rotationally driven, so that the first and second eccentric rollers 9a and 9b rotate eccentrically in the cylinder chambers Sa and Sb. In the first cylinder 6A, the blade 11a is pressed and urged against the spring member 14, and the leading edge thereof slidably contacts the peripheral wall of the eccentric roller 9a to bisect the inside of the first cylinder chamber Sa.

  The refrigerant gas is sucked into the first cylinder chamber Sa from the accumulator 20 through the first suction pipe Pa to be filled. With the eccentric rotation of the eccentric roller 9a, the volume of one of the compartments of the cylinder chamber Sa decreases, and the sucked gas is gradually compressed. When the pressure rises to a predetermined pressure, the discharge valve is opened, and the high-pressure gas is guided into the sealed container 1 through the valve cover.

  The high-pressure gas filled in the sealed container 1 is discharged to the discharge pipe P and guided to the condenser 17. The high-pressure gas is condensed and liquefied in the condenser 17 to be converted into liquid refrigerant, guided to the expansion device 18 and expanded adiabatically, evaporated in the evaporator 19, and takes latent heat of evaporation from the air flowing through the evaporator 19.

  The refrigerant evaporated in the evaporator 19 is led to the accumulator 20 for gas-liquid separation, and the separated low-pressure gas refrigerant is led from the accumulator 20 to the first cylinder chamber Sa via the first suction pipe Pa. It is compressed again and discharged into the sealed container 1 to constitute the refrigeration cycle as described above.

  On the other hand, the low-pressure gas refrigerant separated from the gas and liquid by the accumulator 20 is guided to the second cylinder chamber Sb through the second suction pipe Pb together with the first suction pipe Pa. The second cylinder chamber Sb is filled with a low-pressure gas refrigerant to create a suction pressure (low pressure) atmosphere.

  As described above, the slider 24 in the pressure switching valve K is held at the first operating position, and the oil reservoir 15 and the second blade chamber 10b communicate with each other. The sealed container 1 is filled with the high-pressure gas compressed and discharged in the first cylinder chamber Sa, and the lubricating oil in the oil reservoir 15 at the bottom of the sealed container 1 is affected by high pressure.

  Lubricating oil in the oil reservoir 15 enters the discharge communication passage 28 of the pressure switching valve K and is guided to the blade chamber communication passage 27 through a gap between the notch 30 of the slider 24 and the slider hole 25. Since the blade chamber communication passage 27 communicates with the second blade chamber 10b, the high-pressure lubricating oil fills the second blade chamber 10b and applies a back pressure to the second blade 11b.

  The rear end portion of the second blade 11b is under a discharge pressure (high pressure), while the front end portion is in a low-pressure atmosphere by a low-pressure gas refrigerant guided from the second suction pipe Pb to the second cylinder chamber Sb. . A differential pressure exists at the front and rear end portions of the second blade 11b, and the tip portion of the blade 11b is pressed and biased so as to be in sliding contact with the peripheral wall of the second eccentric roller 9b due to the differential pressure.

  The full capacity in which the same compression action as that of the first cylinder chamber Sa is performed also in the second cylinder chamber Sb, and eventually the compression action is performed in both the first cylinder chamber Sa and the second cylinder chamber Sb. It becomes driving.

When the idle cylinder operation is selected, the energization to the pressure switching valve K is cut off, and the electromagnetic coil 22 is demagnetized.
The magnetic member 23 and the slider 24 receive the elastic force of the compression spring, and the slider 24 is moved and displaced to the second operating position. Therefore, the blade chamber communication passage 27 and the suction communication passage 26 are communicated with the notch 30, and the second blade chamber 10 b and the second suction pipe Pb are communicated with each other via the pressure switching valve K.

  In the first cylinder chamber Sa, the above-described normal compression action is performed, and the high-pressure gas discharged from the discharge pipe P is led to the condenser 17, the expansion device 18, and the evaporator 19 to perform a refrigeration cycle action. Then, the air is sucked into the first cylinder chamber Sa from the accumulator 20 through the first suction pipe Pa and compressed.

  The low-pressure gas refrigerant separated from the gas and liquid by the accumulator 20 is guided to the second cylinder chamber Sb through the second suction pipe Pb together with the first suction pipe Pa. The second cylinder chamber Sb is filled with a low-pressure gas refrigerant, and a suction pressure (low-pressure) atmosphere is created.

  As described above, the slider 24 in the pressure switching valve K is held at the second operating position, and the second suction pipe Pb and the second blade chamber 10b communicate with each other. Accordingly, the second blade chamber 10b is filled with the low-pressure gas refrigerant, and a low-pressure back pressure is applied to the second blade 11b.

The rear end portion of the second blade 11b is under the suction pressure (low pressure), while the front end portion thereof is under a low pressure atmosphere by the gas refrigerant guided from the second suction pipe Pb to the second cylinder chamber Sb. Accordingly, there is no differential pressure at the front and rear end portions of the second blade 11b, and the tip portion of the blade 11b is held by the kicked back by the peripheral wall of the eccentric roller 9b.
Eventually, the compression operation is performed only in the first cylinder chamber Sa, and the compression operation is not performed in the second cylinder chamber Sb.

As described above, since the pressure switching valve K is built in the sealed container 1, piping for switching and introducing the discharge pressure and the suction pressure into the second blade chamber 10b becomes unnecessary, the structure is simplified, and the members This contributes to cost reduction.
During the compression operation in the second cylinder chamber Sb, the discharge pressure is introduced into the second blade chamber 10b by the switching operation of the pressure switching valve K, so that the switching from the compression pause state to the compression operation can be performed in a short time, and the refrigeration Improved cycle efficiency can be obtained.

Further, in order to attach the pressure switching valve K to the second cylinder 6B, it is only necessary to provide a screw hole for a mounting screw, and standardization with the first cylinder 6A is easy.
During the compression action in the second cylinder chamber Sb, since the lubricating oil flows in and out of the second blade chamber 10b due to the reciprocation of the second blade 11b, the blade chamber communication passage 27 and the discharge communication passage 28 have a large cross-sectional area. It is desirable that Further, the suction communication passage 26 may have a small cross-sectional area since there is no gas refrigerant or lubricating oil coming in and out after communicating with the second blade chamber 10b.

  Therefore, as shown in FIGS. 3A, 3B, and 3C, the diameter of the suction communication passage 26 is formed small, and the diameters of the blade chamber communication passage 27 and the discharge communication passage 28 are the same as the diameter of the suction communication passage 26. Formed larger than.

  A blade chamber communication passage 27 communicating with the second blade chamber 10b and a suction communication passage 26 communicating with the second cylinder chamber Sb via the second suction pipe Pb are connected to the slider hole 25 of the pressure switching valve K. Further, a discharge communication path 28 communicating with the inside of the closed container 1 that is the oil reservoir 15 is connected, and a notch 30 is provided in a part of the peripheral surface of the slider 24.

By displacing the slider 24 to the first operating position, the blade chamber communication passage 27 and the discharge communication passage 28 communicate with each other through the notch 30. By displacing the slider 24 to the second operating position, the blade chamber communication path 27 and the suction communication path 26 communicate with each other through the notch 30.
That is, the discharge pressure and the suction pressure guided to the second blade chamber 10b can be switched smoothly and surely while being a simple mechanism that simply reciprocates the slider 24.

An oil reservoir 15 for collecting lubricating oil is provided at the inner bottom of the sealed container 1, and the pressure switching valve K is immersed in the lubricating oil in the oil reservoir 15.
Accordingly, high-pressure lubricating oil can be guided to the second blade chamber 10b, and the lubricating oil is efficiently introduced into the sliding surface between the second blade chamber 10b and the second blade 11b. The slidability of the blade 11b is kept good.

  Further, by immersing the pressure switching valve K in the lubricating oil in the oil reservoir 15, only the lubricating oil leaks into the suction communication passage 26, and the leakage of refrigerant from the discharge pressure side to the suction side is reduced. , Performance degradation is suppressed.

  In order to introduce a high pressure to the second blade chamber 10b, the discharge communication passage 28 provided in the pressure switching valve K is opened in the lubricating oil. Since the lubricating oil enters and exits the second blade chamber 10b by the second blade 11b reciprocating during the compression action, the resistance is reduced, and the movement of the second blade 11b is smooth and the loss is reduced.

Next, the pressure switching valve Ka in the second embodiment will be described.
FIG. 4 is a longitudinal sectional view of an essential part of the hermetic compressor R provided with a pressure switching valve Ka. 5 and 6 are enlarged longitudinal sectional views of the pressure switching valve Ka in different states.

Since the configuration of the hermetic compressor R excluding the pressure switching valve Ka described later is the same as that shown in FIG. 1, FIG. 1 is applied here, and in FIG. Thus, a new description is omitted.
FIG. 4 shows an outline of the pressure switching valve Ka, in which only some components are denoted by reference numerals, details are shown in FIGS. 5 and 6, and all component parts are denoted by reference numerals.

The pressure switching valve Ka includes a valve body 21A, a magnetic member 23A, a slider 24A, an electromagnetic coil 22A, and a cylindrical member 31 made of a nonmagnetic material.
The valve body 21A is attached to the lower surface of the second cylinder 6B so as to close the lower open surface of the second blade chamber 10b. A slider hole 25A is provided through the left and right end faces of the valve body 21A, and the slider 24A is slidably received in the slider hole 25A.

  The end face of the slider hole 25A is opened to the oil reservoir 15 in the sealed container 1 to form a discharge communication path 28A. The slider hole 25A and the second blade chamber 10b communicate with each other through a blade chamber communication path 27A. The second suction pipe Pb connected to the second cylinder chamber Sb and the slider hole 25A communicate with each other through a suction communication passage 26A formed across the valve body 21A and the valve body 21A.

  Here, the diameter of the suction communication path 26A is formed to be the smallest, the diameter of the blade chamber communication path 27A is formed larger than the diameter of the suction communication path 26A, and the diameter of the discharge communication path 28A is the diameter of the blade chamber communication path 27A. Than is formed.

  A groove portion 32 is provided on the end surface opposite to the end surface where the discharge communication passage 28A of the valve body 21A is opened and along the slider hole 25A, and the end portion of the cylindrical member 31 is fitted and fixed. The The cylindrical member 31 is inserted from the outside of the sealed container 1 into an insertion hole 33 provided in the sealed container 1, and the tip opening is engaged and fixed to the groove 32 of the valve body 21A.

  A narrow gap is formed between the end face of the valve main body 21A and the inner peripheral wall of the sealed container 1, and a part of the cylindrical member 31 is exposed. An oil hole 34 composed of a plurality of small holes is provided in the exposed portion of the cylindrical member 31 so that the outer surface side and the inside of the cylindrical member 31 communicate with each other. That is, the lubricating oil is guided into the cylindrical member 31 from the oil hole 34, and the smooth movement of the slider 24 is ensured as will be described later.

  The insertion hole 33 of the hermetic container 1 and the circumferential surface of the cylindrical member 31 inserted therethrough are brazed using a brazing material (seal material) and are completely sealed. The closed end surface of the cylindrical member 31 protrudes to the outside of the sealed container 1, and the electromagnetic coil 22 </ b> A is fitted and fixed to the outer peripheral surface of the end portion.

  Further, the compression spring 35 is inserted into the end of the cylindrical member 31 and comes into contact with the end surface of the magnetic member 23 </ b> A inserted into the cylindrical member 31. The magnetic member 23A is formed in a slidable diameter in the cylindrical member 31, and the slider 24A is integrally provided continuously.

  The slider 24A has a flange portion d formed in a small diameter with a gap between the inner diameter of the cylindrical member 31 and the gap between the base end portion connected to the magnetic member 23A and the fitting portion between the cylindrical member 31 and the valve body 21A. Have. A sliding contact portion e is integrally connected to both ends of the notch portion 30A at the front end of the flange portion d with the notch portion 30A interposed therebetween.

  The sliding contact portion e is slidably fitted into the slider hole 25A. The notch 30A is smaller than the diameter of the slider hole 25A and is designed to have the same diameter as the flange d. Therefore, a narrow gap is formed between the peripheral surface of the notch 30A and the peripheral surface of the slider hole 25A, and between the peripheral surface of the flange d and the inner peripheral surface of the cylindrical member 31.

  When the electromagnetic coil 22A is energized and the magnetic member 23A is magnetically attracted against the elastic force of the compression spring 35, as shown in FIG. 5, the notch 30A faces the suction communication path 26A, but the slider 24A The front end surface is retracted to a position where the blade chamber communication passage 27A of the valve body 21A is opened. The position of the slider 24A at this time is referred to as a “first operation position”.

If the electromagnetic coil 22B is disconnected, the magnetic attraction action on the magnetic member 23A is lost. Instead, the elastic force of the compression spring 35 acts, and as shown in FIG. 6, the end surface of the slider 24A moves over the blade chamber communication passage 27A to a position near the end surface of the valve body 21A.
As a result, the discharge communication passage 28A, which is an opening formed in the end face of the valve body 21A, is closed. At the same time, the notch 30A of the slider 24A is at a position facing both the blade chamber communication path 27A and the suction communication path 26A.

  The position of the slider 24A at this time is referred to as a “second operating position”. Note that the oil hole 34 provided in the cylindrical member 31 is always closed without being closed by the slider 24A regardless of the position movement of the slider 24A.

When the pressure switching valve Ka configured as described above is selected for normal operation, the electromagnetic coil 22A of the pressure switching valve Ka is energized, and the magnetic member 23A and the slider 24A resist the elastic force of the compression spring 35. Magnetically attracted.
The slider 24A is moved and displaced to the first operating position shown in FIG. 5, and the blade chamber communication path 27A and the discharge communication path 28A are communicated. Therefore, the second blade chamber 10B and the oil reservoir 15 are communicated with each other via the pressure switching valve Ka.

An operation signal is sent to the electric motor unit 4, the rotary shaft 5 is driven to rotate, and a compression action is performed in the first cylinder chamber Sa. The sealed container 1 is filled with a compressed gas refrigerant and further discharged from the closed compressor R to the discharge pipe P to constitute a refrigeration cycle.
The low-pressure gas refrigerant separated from the gas and liquid by the accumulator 20 is guided to the second cylinder chamber Sb through the second suction pipe Pb together with the first suction pipe Pa. The second cylinder chamber Sb is filled with a low-pressure gas refrigerant, and a suction pressure (low-pressure) atmosphere is created.

  On the other hand, the slider 24A in the pressure switching valve Ka is held in the first operating position, and the lubricating oil in the oil reservoir 15 is guided from the discharge communication passage 28A of the pressure switching valve Ka to the blade chamber communication passage 27A. The second blade chamber 10b is filled, and a discharge pressure (high pressure) back pressure is applied to the second blade 11b.

  The second blade 11b has a differential pressure at the front and rear end portions, and due to the differential pressure, the tip portion of the blade 11b is pressed and urged so as to be in sliding contact with the peripheral wall of the eccentric roller 9b. The full capacity in which the same compression action as that of the first cylinder chamber Sa is performed also in the second cylinder chamber Sb, and eventually the compression action is performed in both the first cylinder chamber Sa and the second cylinder chamber Sb. It becomes driving.

  When the idle cylinder operation is selected, the energization of the electromagnetic coil 22A is cut off, and the magnetic member 23A and the slider 24A receive the elastic force of the compression spring 35. Since the slider 24A is in the second operating position shown in FIG. 6, the blade chamber communication passage 27A and the suction communication passage 26A communicate with each other via the notch 30A, and the second blade chamber 10b and the second suction pipe Pb are connected. Is communicated.

  The low-pressure gas refrigerant separated from the gas and liquid by the accumulator 20 is guided to the second cylinder chamber Sb through the second suction pipe Pb together with the first suction pipe Pa. The second cylinder chamber Sb is filled with a low-pressure gas refrigerant, and a suction pressure (low-pressure) atmosphere is created.

  Since the slider 24A in the pressure switching valve Ka is held at the second operating position and the second suction pipe Pb and the second blade chamber 10b communicate with each other, the second blade chamber 10b has a low-pressure gas. The refrigerant is filled with a low-pressure atmosphere, and a suction pressure (low pressure) back pressure is applied to the second blade 11b.

  The rear end of the second blade 11b is under the suction pressure (low pressure), while the front end is under the low pressure atmosphere of the second cylinder chamber Sb. Accordingly, there is no differential pressure at the front and rear ends of the second blade 11b, and the eccentric roller 9b rotates idly. Eventually, the compression action is performed only in the first cylinder chamber Sa, and the capacity half operation is not performed in the second cylinder chamber Sb.

  Also here, the slider 24A can be reciprocated with a relatively simple configuration by combining the magnetic member 23A and the electromagnetic coil 22A. Since the electromagnetic coil 22A is attached to the outer space of the sealed container 1, it is not necessary to attach a sealed terminal for energization to the sealed container 1, and the wiring configuration can be simplified.

  Since it is not necessary to immerse the electromagnetic coil 22A in the lubricating oil in the oil reservoir 15, it is not necessary to provide the electromagnetic coil 22A with oil resistance and refrigerant resistance. Since the cylindrical member 31 that accommodates the magnetic member 23A and the slider 24A is fitted and fixed in the groove portion 32 provided in the valve body 21A, the slider hole 25A and the slider 24A can be easily centered, and the assemblability is good. .

  In order to assemble the pressure switching valve Ka to the hermetic compressor R in the above-described embodiment, first, only the valve main body 21A of the pressure switching valve Ka is attached to the second compression mechanism section 3B. And housed in a sealed container 1.

  Then, the cylindrical member 31 containing the slider 24A, the magnetic member 23A, and the compression spring 35 is inserted through the insertion hole 33 provided in the sealed container 1, and this end is fitted into the groove 32 of the valve body 21A. Fix it. Thereafter, the insertion hole 33 of the sealed container 1 and the peripheral surface of the insertion portion of the cylindrical member 31 are sealed by brazing.

  The electromagnetic coil 22A may be attached to the cylindrical member 31 in advance, or may be attached after the compressor is assembled. Therefore, the pressure switching valve Ka can be assembled only by adding to the conventional compressor assembling method without requiring a special assembling process or a special hermetic container, and the increase in man-hours can be minimized.

  The cylindrical member 31 is preferably made of a nonmagnetic material so that the electromagnetic coil 22A magnetically attracts the magnetic member 23A. However, if the magnetic member 23A can operate normally, the cylindrical member 31 has some magnetism. May be.

FIG. 7 is a cross-sectional plan view of the hermetic compressor R for explaining the pressure switching valve Ka according to the third embodiment.
Since the operation is the same as that described in the second embodiment, the description of the operation is omitted and only the configuration will be described.

  The pressure switching valve Ka is provided in the intermediate partition plate 2 interposed between the first cylinder 6A and the second cylinder 6B. That is, a slider hole 25B is provided from a part of the outer peripheral surface of the intermediate partition plate 2 to a position facing the second blade chamber 10b, and the slider 24A, the magnetic member 23A and the cylindrical member 31 containing the compression spring 35 are attached. It is done.

The slider hole 25B has a blade chamber communication passage (not shown) communicating with the second blade chamber 10b, a suction communication passage 26A communicating with the second suction pipe Pb, and a discharge communication opening in the sealed container 1. A passage (not shown) is provided.
The upper surface of the second blade chamber 10b is closed by the intermediate partition plate 2, but the lower surface is open in the sealed container 1 and exposed to the discharge pressure, so some kind of closing member is necessary.

  If it is the above structure, the said intermediate partition plate 2 will also serve as the valve body with which the pressure switching valve Ka is originally provided. Therefore, the number of parts is reduced, the man-hours for attaching the valve body and the processing of the screw holes for attachment to the second cylinder 6B become unnecessary, and the influence on the cost can be suppressed.

The hermetic compressor R is configured to connect the first suction pipe Pa and the second suction pipe Pb independent to each of the first cylinder chamber Sa and the second cylinder chamber Sb. It is not limited to this.
FIG. 8 is a longitudinal sectional view of a main part of a hermetic compressor R as a fourth embodiment.

Instead of the first and second suction pipes Pa and Pb, a type in which one suction pipe P is connected to a suction guide path 40 provided in the intermediate partition plate 2A may be used.
The suction guide path 40 is branched into two guide paths 40a and 40b inside the intermediate partition plate 2A, one branch guide path 40a communicates with the first cylinder chamber Sa, and the other branch guide path 40b is the first. It is formed to communicate with the two cylinder chambers Sb.

The pressure switching valve Ka used here has the same configuration as that described in the second embodiment based on FIGS. 4, 5 and 6, and is attached at the same position.
However, a hole 42 for communicating the suction communication path 26A provided in the valve main body 21A and the suction guide path 40 provided in the intermediate partition plate 2 is provided through the upper and lower end surfaces of the second cylinder 6B. Also, it is necessary to provide the intermediate partition plate 2A.

  The pressure switching valve K described above includes an electromagnetic coil 22, a magnetic member 23, and a slider 24 integrally connected to the magnetic member 23, and is configured to reciprocate the slider 24 in the axial direction. However, it is not limited to this.

As a fifth embodiment, a pressure switching valve K as shown in FIGS. 9A and 9B may be used.
That is, a first cutout portion 30Da in which a part of the peripheral surface of the rotating shaft 24D is cut out is provided, and the first cutout portion 30Da is a peripheral surface portion that faces 180 ° and is axially The second notch 30Db is provided with the position shifted. The end of the rotation shaft 24D is connected to an actuator 50 such as a pulse motor.

  In the valve body 21D, a suction communication passage 26D and a blade chamber communication passage 27D are provided at a predetermined interval from the same side surface over the slider hole 25D. A discharge communication path 28D is provided from the opposite side surface to the slider hole 25D with a predetermined distance from the blade chamber communication path 27D.

  Therefore, as shown in FIG. 9A, the first notch 30Da in the rotation shaft 24D can communicate the suction communication path 26D and the blade chamber communication path 27. Further, if the rotation shaft 24D is rotated 180 °, the second notch 30Db communicates the blade chamber communication path 27D and the discharge communication path 28D.

  With the pressure switching valve Ka having such a configuration, the protruding amount of the actuator 50 from the valve body 21D can be suppressed to a minimum. Further, an actuator having oil resistance and refrigerant resistance can be accommodated in the hermetic container 1, and it is not necessary to secure an external space.

  In the above-described embodiment, in order to perform the cylinder resting operation (capability half operation), the slider 24 is displaced to the “second operating position”. For this purpose, the energization of the electromagnetic coil 22 is cut off, the magnetic attraction action on the slider 24 and the magnetic member 23 is eliminated, and the elastic force of the compression spring 35 is applied to the slider 24 instead.

In this second operating position, the position of the slider 24 must be displaced and stopped so that the notch 30 of the slider 24 is surely opposed to the blade chamber communication path 27 and the suction communication path 26.
As a sixth embodiment, positioning means for the slider 24A when the slider 24A is displaced to the second operating position will be described.

  FIGS. 10A and 10B are schematic longitudinal sectional views of a pressure switching valve Kb in the sixth embodiment and a part of a hermetic compressor provided with the pressure switching valve Kb. FIG. 10A shows the state during full capacity operation, and FIG. 10B shows the state during half capacity operation.

  The basic configuration of the pressure switching valve Kb used in this embodiment employs the basic configuration of the pressure switching valve Ka described in the second embodiment (FIGS. 4 to 6). The intermediate partition plate 2A and the suction guide path 40 provided in the intermediate partition plate 2A are the same as those described in the fourth embodiment (FIG. 8).

  The pressure switching valve Kb is fixed to the valve body 21B, the magnetic member 23A, the slider 24A integrally formed with or coupled to the magnetic member 23A, the electromagnetic coil 22B, the cylindrical member 31 made of a non-magnetic material, and the cylindrical member 31. The permanent magnet 31A as a slider holding member.

  The electromagnetic coil 22B used here is not of the type that is switched and controlled by the presence or absence of energization as described above, but is a so-called self-holding type that maintains its state by switching to the opposite polarity.

  The valve body 21B is attached to the lower surface of the second cylinder 6B so as to close the lower open surface of the second blade chamber 10b, and the cylindrical member 31 is connected to the valve body 21B. A slider hole 25A is provided between the valve body 21B and the cylindrical member 31, and the slider 24A is slidably accommodated in the slider hole 25A.

  The end face of the valve body 21B is provided with a hole having a diameter smaller than the diameter of the slider hole 25A, which is referred to as a discharge communication path 28A. Since the diameter of the discharge communication passage 28A is smaller than the diameter of the slider hole 25A, the stepped portion 60, which is a slider positioning means, is provided at the end of the valve body 21B.

  The slider 24 </ b> A is provided with a through hole 61 at the center axis position along the axial direction, and both ends of the slider 24 </ b> A have the same atmosphere through the through hole 61. That is, by providing the through hole 61, both end portions of the slider 24A can maintain the same pressure, and a pressure balance can be obtained.

  Similar to the embodiment described above, in this embodiment, the suction pressure is introduced into the second blade chamber 10b to enable the cylinder resting operation for the second cylinder chamber Sb. A permanent magnet Z is attached along the peripheral surface of the chamber 10b where the second blade 11b contacts and is separated.

Only the points described above are different from the configuration described in the second embodiment, and the other components are basically the same, and thus the same reference numerals are given and new descriptions are omitted.
When the normal operation is selected, the electromagnetic coil 22B is energized, and the magnetic member 23A is magnetically attracted against the elastic force of the compression spring 35 as the slider urging member.

  As shown in FIG. 10A, the end face of the slider 24A is retracted to a position where the blade chamber communication passage 27A of the valve body 21A is opened, and the first operation of communicating the blade chamber communication passage 27A and the discharge communication passage 28A. Displace to "position". Even if the energization of the electromagnetic coil 22B is stopped in this state, the magnetic member 23A is attracted to the permanent magnet 31A, and the position of the slider 24A is maintained.

  The discharge pressure (high pressure) in the hermetic container 1 is guided from the discharge communication passage 28A of the pressure switching valve Kb to the second blade chamber 10b via the blade chamber communication passage 27A, and has a high pressure with respect to the second blade 11b. Back pressure is applied. Therefore, a differential pressure is generated at the front and rear end portions of the second blade 11b, and the full capacity operation that performs the compression action is performed also in the second cylinder chamber Sb.

  At this time, the notch 30A of the slider 24A is displaced from the position facing the suction communication path 26A, and this point is different from that of the second embodiment (FIG. 5). 26A is closed by the slider 24A.

When the idle cylinder operation is selected, the electromagnetic coil 22B is switched to the reverse polarity, the repulsive force acts on the slider 24A together with the magnetic member 23A, the elastic force of the compression spring 35 acts, and the permanent magnet 31A overcomes the attractive force. The slider 24A moves.
As shown in FIG. 10 (B), the front end surface of the slider 24A passes over the blade chamber communication passage 27A and is bumped by a stepped portion 60 provided on the end surface of the valve body 21B. In this state, even if energization of the electromagnetic coil 22B is stopped, the position of the slider 24A is held by the elastic force of the compression spring 35.

  The slider 24A is positioned by the step portion 60, blocks the discharge communication path 28A and the outer peripheral surface of the valve body 21B, and closes the discharge communication path 28A and the blade chamber communication path 27A that have been communicated so far. . On the other hand, the blade chamber communication passage 27A and the suction communication passage 26A communicate with each other through the notch 30A of the slider 24A, and the displacement is shifted to the “second operating position”.

  The suction pressure (low pressure) introduced from the accumulator 20 is guided to the second blade chamber 10b via the suction communication passage 26A and the blade chamber communication passage 27A of the pressure switching valve Kb, and is low in pressure with respect to the second blade 11b. The back pressure is applied.

  The second blade 11b has the same low pressure at the front and rear ends, the front end is kicked by the eccentric roller 9b and retracted into the second blade chamber 10b, and the rear end is magnetically attracted to the permanent magnet Z, and the position thereof is increased. Hold. In the second cylinder chamber Sb, a half capacity operation is performed in which the compression action stops.

  Thus, in order to adjust the pressure with respect to the second blade chamber 10b in the sealed container 1 by the pressure switching valve Kb, the pressure switching valve Kb needs to be further downsized. Therefore, if the slider 24A can always be accurately positioned, the required stroke including the tolerance of the slider 24A can be reduced, and the pressure switching valve Kb can be downsized.

  However, at the position where the second blade chamber 10b and the suction communication passage 26A communicate with each other, the surrounding area may be a discharge pressure atmosphere, and there are many high and low pressure seal portions, and if the slider 24A is not positioned accurately, the amount of leakage is large. As a result, performance is degraded.

  According to the embodiment described above, the step portion (slider positioning means) 60 is provided so that the slider 24A of the pressure switching valve Kb is restrained at a position where the second blade chamber 10b and the suction communication passage 26A communicate with each other. Therefore, the pressure switching valve Kb can be downsized. In addition, the leakage amount can be reduced and the performance can be improved.

Further, at least a part of the pressure switching valve Kb can be incorporated as the hermetic compressor R, and no external piping is required, so that cost reduction can be realized. The step portion 60 may be formed by providing a slider hole 25A in the valve body 21A and processing only the end of the valve body 21A, or by using a separate piece.
In any case, the provision of the step portion 60 as the positioning means for the slider 24A makes it easy to ensure the positional accuracy of the slider 24A and enables more accurate positioning.

  In this embodiment, the self-holding type of the electromagnetic coil 22B that is energized only when the position of the slider 24A is moved and switched to the reverse polarity is used. In contrast to the type controlled by the presence / absence of energization described in the previous embodiment, the same effect can be obtained by energizing only at the time of switching, and the power consumption can be greatly reduced.

  By providing the through holes 61 along the axial direction of the slider 24A, the pressures at both ends of the slider 24A can always be kept the same. Therefore, the movement of the position of the slider 24A is smoothly started, and the operation reliability can be improved.

  FIG. 11 is a schematic longitudinal sectional view of a pressure switching valve Kc and a part of a hermetic compressor provided with the pressure switching valve Kc, showing a first modification example of the sixth embodiment. The state during operation (full capacity operation) is shown.

The slider hole 25B provided in the valve main body 21C is opened with the same diameter at the end of the valve main body 21C to form a discharge communication path 28A. The end f of the valve main body 21 </ b> C protrudes in the axial direction, particularly in a part on the upper side, and abuts on the circumferential surface of the flange 8 a of the auxiliary bearing 8. The projecting length of the projecting portion f is substantially the same as the plate thickness of the valve cover 12 fitted into the peripheral surface of the flange portion 8a of the auxiliary bearing 8.
There is no change in the structure of the slider 24A itself, the electromagnetic coil 22B attached to the slider 24A, the magnetic member 23A, and the compression spring 35. Since other configurations are the same as those shown in FIGS. 10A and 10B, the same reference numerals are given and new descriptions are omitted.

  During the idle cylinder operation, the slider 24A moves to the left from the state shown in the figure by switching to the reverse polarity with respect to the electromagnetic coil 22B, and finally the end of the slider 24A is stopped by the valve cover 12. That is, here, the valve cover 12 constitutes a positioning means for the slider 24A, and positions the slider 24A at the second operating position.

  In this way, the slider main body 21C is not provided with the slider positioning means, but can be shared by the valve cover 12 which is an existing part, and the influence on the cost is suppressed. Further, by closing the pressure switching valve Kc itself against the outer peripheral surface of the sub-bearing 8, the closing performance of the second blade chamber 10b is improved.

  FIG. 12 is a schematic longitudinal sectional view of a pressure switching valve Kd and a part of a hermetic compressor provided with the pressure switching valve Kd, showing a second modification of the sixth embodiment. The state during operation (full capacity operation) is shown.

A part of the auxiliary bearing 8A is extended to a position in the vicinity of the inner peripheral wall of the sealed container 1, which is a part provided with the original valve body, and the auxiliary bearing 8A is configured to also use a part of the pressure switching valve Kd. A slider hole 25C is provided from the outer peripheral surface of the extension portion of the auxiliary bearing 8A toward the axis, and the end of the slider hole 25C serves as a slider positioning means.
Further, a suction communication path 26A, a blade chamber communication path 27A, and a discharge communication path 28A are provided in an extension portion of the auxiliary bearing 8A.

  There is no change in the structure of the slider 24A itself, the electromagnetic coil 22B attached to the slider 24A, the magnetic member 23A, and the compression spring 35. Since other configurations are the same as those shown in FIGS. 10A and 10B, the same reference numerals are given and new descriptions are omitted.

  During idle cylinder operation, the slider 24A moves to the left from the state shown in the figure by switching to the opposite polarity with respect to the electromagnetic coil 22B. Finally, the end of the slider 24A is the end face of the slider hole 25C which is the slider positioning means. And is positioned at the second operating position.

  Also here, the slider positioning means can be shared by the existing auxiliary bearing 8A, which suppresses the influence on the cost. The space efficiency is improved, the pressure switching valve Kd is easily built in, and the degree of freedom in design can be improved. By closing the pressure switching valve Kd itself against the end face of the slider hole 24C of the auxiliary bearing 8A, the closing performance of the second blade chamber 10b is improved.

  In the pressure switching valves Ka to Kd provided with the cylindrical member 31 described above, the cylindrical member 31 is attached to the sealed container 1 by brazing, but the present invention is not limited to this and is described below. May be.

FIGS. 13 (A), (B) and FIGS. 14 (A), (B) are schematic views of the pressure switching valve Ke in the seventh embodiment and a part of the hermetic compressor provided with the pressure switching valve Ke. It is a longitudinal cross-sectional view and a schematic cross-sectional view.
FIGS. 13A and 13B show the state at the time of half capacity operation, and FIGS. 14A and 14B show the state at the time of full capacity operation.

  In the above-described embodiment, the idle cylinder operation is performed for the second cylinder chamber Sb at the time of half capacity operation. Here, the idle cylinder operation is performed for the first cylinder chamber Sa. It is configured.

  A second blade chamber 10b is provided in the second cylinder 6B, and a second blade 11b and a spring member 14 that is a compression spring that always applies a back pressure to the second blade 11b are accommodated. Therefore, the tip of the second blade 11b is always in contact with the second eccentric roller 9b accommodated in the second cylinder chamber Sb.

A slider hole 25D is provided from the outer peripheral surface of the intermediate partition plate 2A to a hole portion through which the rotary shaft is inserted, and the slider 24A is inserted therein. Specifically, the airtight container 1 is provided with an attachment hole, and one end of the guide pipe 70 is attached. The other end of the guide pipe 70 protrudes from the sealed container 1 to the outside with a necessary minimum length.
A cylindrical member 31 made of a non-magnetic material is inserted into the guide pipe 70, and the cylindrical member 31 is bonded and fixed to the guide pipe 70 by high frequency induction heating.

  Compared with brazing the cylindrical member 31 to the closed container 1 (or the guide pipe 70) as described above, the high-frequency induction heating can perform uniform heating in a short time. Accordingly, it is possible to secure the concentricity between the slider hole 25 </ b> D and the cylindrical member 31 by performing mounting and fixing that reliably prevents thermal deformation of the cylindrical member 31.

  One end of the cylindrical member 31 is inserted into the sealed container 1 and press-fitted into a step provided on the peripheral surface of the slider hole 25D of the intermediate partition plate 2A. The other end of the cylindrical member 31 protrudes outside from the sealed container 1, and an electromagnetic coil 22B is attached to this end, and the end of the cylindrical member 31 is closed by the electromagnetic coil 22B.

  The slider 24A, the magnetic member 23A provided integrally with the slider 24A or connected as a separate part, and the compression spring 35 are accommodated from the slider hole 25D to the inside of the cylindrical member 31. A stopper pin 72 is provided at a predetermined portion of the slider hole 25D across the slider hole 25D.

  A suction pipe P extending from the accumulator 20 passes through the sealed container 1 and is connected to a suction guide path 40 provided in the intermediate partition plate 2A. The suction guide path 40 is branched into two guide paths 40a and 40b. One branch guide path 40a communicates with the first cylinder chamber Sa, and the other branch guide path 40b communicates with the second cylinder chamber Sb. This is as described above.

  In this embodiment, a lateral hole 73 is provided from the side surface portion of the intermediate partition plate 2A, penetrates from the peripheral surface portion of the slider hole 25D to the opposing peripheral surface portion via the shaft core, and further the suction It is provided so as to communicate with the guide path 40.

  Note that the intermediate partition plate 2 </ b> A portion of the lateral hole 73 is closed by a plug 74. Accordingly, the lateral hole 73 forms a suction communication path 26B that allows the slider hole 25D and the suction guide path 40 to communicate with each other.

  The suction communication path 26B is composed of a lateral hole 73a provided from the side surface on the opposite side of the intermediate partition plate 2A to the slider hole 25D via the suction guide path 40, as shown by a two-dot chain line in the figure. Also good.

  However, it is necessary to select a position where the portion from the side surface portion of the intermediate partition plate 2A to the suction guide path 40 of the horizontal hole 73a is blocked by the peripheral surface portion of the suction pipe P that is inserted into and connected to the suction guide path 40. There is. Eventually, the suction hole 26 </ b> B that connects the slider hole 25 </ b> D and the suction guide path 40 is also formed by the lateral hole 73 a.

  The intermediate partition plate 2A is provided with a blade chamber communication passage 27B that communicates the slider hole 25D with the first blade chamber 10a. Further, the intermediate partition plate 2A and the first cylinder 6A include a slider chamber. A discharge communication path 28 </ b> B that communicates the hole 25 </ b> D and the inside of the sealed container 1 is provided.

  13A and 13B, the slider 24A is in the second operating position, and the suction communication path 26B is provided via the notch 30A of the slider 24A and the slider hole 25D. And the blade chamber communication passage 27B communicate with each other. The suction pressure (low pressure) is guided to the first blade chamber 10a, and the cylinder resting operation (capacity half operation) is performed in the first cylinder chamber Sa.

  As shown in FIGS. 14A and 14B, when the energization to the electromagnetic coil 22B is interrupted, the elastic force of the compression spring 35 acts, and the slider 24A is slid and biased in the direction of the central axis of the intermediate partition plate 2A. . The tip of the slider 24A is stopped by the stopper pin 72 and positioned at the first operating position.

  In this state, the blade chamber communication passage 27B and the discharge communication passage 28B communicate with each other through the notch 30A of the slider 24A and the slider hole 25D, and the discharge pressure (high pressure) in the hermetic container 1 is changed to the first blade chamber 10a. Led to. Accordingly, the normal operation (full capacity operation) is performed in which the compression action is performed in the first cylinder chamber Sa together with the second cylinder chamber Sb.

  As described above, the guide pipe 70 is provided in the hermetic container 1, and the cylindrical member 31 constituting the pressure switching valve Ke is bonded and fixed to the guide pipe 70 by high-frequency induction heating. Thus, uniform heating can be performed. The thermal deformation of the cylindrical member 31 can be reliably prevented, and the concentricity between the slider hole 25D and the cylindrical member 31 can be ensured.

  Therefore, the malfunction of the slider 24A accommodated in the cylindrical member 31 can be prevented, and the reliability can be improved. Moreover, since the guide pipe 70 is provided in the sealed container 1, the cylindrical member 31 can be easily attached to the sealed container without increasing the heating amount.

FIG. 15 is a modification of the seventh embodiment.
Only the configuration different from that of the seventh embodiment will be described, and FIGS. 13 and 14 will be applied to the same components and the same configurations, and the description will be omitted by assigning the same numbers.

For the guide pipe 70 provided in the sealed container 1, a material having a Young's modulus (material or form having low rigidity) smaller than that of the sealed container 1 is selected. The cylindrical member 31 is secured an auxiliary pipe 75, the auxiliary pipe 75 is constituted by a small Young's modulus than the cylindrical member 31 material (material or form rigidity is small).

The cylindrical member 31 is attached to the sealed container 1 by joining and fixing the guide pipe 70 and the auxiliary pipe 75 by brazing.
That is, the guide pipe 70 and the auxiliary pipe 75 are heated at the time of brazing, but these are made of a material having low rigidity, so that the cylindrical member 31 attached to the sealed container 1 can be prevented from being deformed. Therefore, the malfunction of the slider 24A accommodated in the cylindrical member 31 can be prevented, and the reliability can be improved.

The guide pipe 70 and the auxiliary pipe 75 are both selected from copper pipes, and it goes without saying that the above-described effects can be obtained even if the guide pipe 70 and the auxiliary pipe 75 are joined and fixed by copper brazing. Yes.

  In the seventh embodiment, the target of the cylinder resting operation is the first cylinder chamber Sa, and in the other embodiments, the second cylinder chamber Sb is permanently attached to the blade chambers 10a and 10b acting on the cylinder chamber Sa. The magnet Z is attached, and the rear end portions of the blades 11a and 11b accommodated in the blade chambers 10a and 10b are magnetically attracted during the cylinder resting operation.

  Originally, a force due to the differential pressure between the discharge pressure and the suction pressure does not act on the blade during the cylinder resting operation in which the compression action is stopped, and is pushed to the outer diameter side by the eccentric roller. However, there may be slight movement due to pressure pulsation caused by gas agitation in the cylinder chamber, leading to noise generation. To prevent this, the blade is magnetically adsorbed by a permanent magnet.

For example, in Japanese Patent Application Laid-Open No. 2004-301114, a lateral hole for attaching a permanent magnet is provided from the side surface of the cylinder to the blade chamber. A configuration is disclosed in which one end surface of the permanent magnet inserted into the horizontal hole is flush with the cylinder side surface, and the other end surface protrudes into the blade chamber and is fixedly mounted.
The blade has a vertically long plate shape, whereas the permanent magnets are magnetically attracted to the blade, and in order to securely attach and fix to the cylinder, the cylindrical shape with the axial direction from the cylinder end face toward the blade chamber Is used.

According to the above disclosed technique, since the large-diameter lateral hole is provided in the thickness of the cylinder, the remaining thickness of the cylinder is reduced, the rigidity is lowered, and deformation is likely to occur during processing and assembly.
The permanent magnet formed into a cylindrical shape is magnetized in the radial direction, but there is no magnetic member on the outer peripheral side. Therefore, the resistance of the magnetic circuit is large, the magnetic flux is small, and a sufficient magnetic force cannot be generated. In order to obtain a predetermined magnetic force, there is another problem that the permanent magnet must be enlarged.

In the eighth embodiment, in consideration of the above problems, the permanent magnet mounting structure in the blade chamber is improved.
Hereinafter, for example, the second blade chamber 10b will be described as an object, but there is no problem even if the object is changed to the first blade chamber 10a.

  As shown in FIG. 16, a second blade chamber 10b is provided in the second cylinder 6B. The blade chamber 10b is opened to the second cylinder chamber Sb formed in the inner diameter portion of the second cylinder 6B, and a groove portion 10b1 provided along the outer diameter direction of the second cylinder 6B. It consists of the vertical hole part 10b2 provided in the edge part of 10b1.

  Both the groove portion 10b1 and the vertical hole portion 10b2 constituting the second blade chamber 10b are provided through the upper and lower surfaces in the thickness direction of the cylinder 6B from the upper surface to the lower surface of the second cylinder 6B. .

  The second blade 11b is movably accommodated across the groove 10b1 and the vertical hole 10b2. In other words, in order to prevent gas leakage from the second cylinder chamber Sb, both side surfaces of the second blade 11b are fitted into the both side surfaces of the groove 10b1 with almost no gap and move in a sliding contact state.

  A permanent magnet Z having a width dimension substantially the same as the width dimension of the blade 11b is attached along the plate thickness direction of the cylinder 6B to the peripheral surface portion facing the groove section 10b1 in the vertical hole section 10b2 in the second blade chamber 10b. It is done. The permanent magnet Z may be attached to the vertical hole portion 10b2 using an adhesive, or using a holding member as described later.

  The second blade 11b is formed in such a length that the rear end portion adheres to the permanent magnet Z when the tip end portion is in a position where it slightly sinks from the peripheral surface of the second cylinder chamber Sb. The length in the longitudinal direction, which is the front-rear direction of the paper surface, is the same as the thickness of the second cylinder.

  Thus, by attaching the permanent magnet Z in the blade chamber 10b and magnetically adsorbing the blade 11b, a magnetic circuit extending from the cylinder 6B to the permanent magnet Z to the blade 11b is formed, and the magnetic force of the permanent magnet Z can be used efficiently. As a result, the amount of permanent magnet Z used can be reduced.

  In order to attach the permanent magnet Z, it is not necessary to process the cylinder 6B or the blade chamber 10b, the number of processing steps is reduced, and the cylinder 6B is not scraped, so that a reduction in rigidity of the cylinder 6B can be avoided.

FIGS. 17A and 17B and FIGS. 18A, 18B, and 18C are modifications of the eighth embodiment.
FIG. 17A is a plan view of the first holding member 80A that holds the second blade 11b in the second blade chamber 10b, and FIG. 17B shows the second blade 11b in the second blade chamber. It is a top view of the 2nd holding member 80B hold | maintained to 10b.
18A is a perspective view of the first holding member, FIG. 18B is a front view of the first holding member, and FIG. 18C is a side view of the first holding member.

  The first holding member 80A is formed in a substantially letter “E” shape from a pair of horizontal pieces that are spaced apart in the vertical direction and a vertical piece that connects the central portions of the pair of horizontal pieces. A base part g provided with a piece projecting downward from the center of the piece, a bent part m bent integrally from both ends of the horizontal piece of the base part g, and a holding protrusion h described later provided on the base part g It consists of.

  The holding protrusion h has a pair of protrusions that are cut in a direction opposite to the bending direction of the bending portion m, with a predetermined interval in the vertical direction at the center of the vertical piece of the base portion g, and the protruding portion. It is comprised from the bending piece bent along the both-sides edge of the base | substrate part g in the site | part which opposes mutually, and bend | folded in the direction opposite to the bending direction of the bending part m. The protrusion (bending) height of the holding protrusion h is set to be larger than the thickness of the permanent magnet Z.

  The permanent magnet Z is inserted and held between the pair of protrusions constituting the holding protrusion h and the bent piece. In order to ensure reliability, it is preferable to apply an adhesive between the holding projection h and the permanent magnet Z. The end edge protrudes from the surface of the permanent magnet Z by setting the protrusion height of the holding protrusion h.

  Then, the first holding member 80A holding the permanent magnet Z is inserted and attached to the second blade chamber 10b. Also at this time, it is preferable to apply an adhesive to the bent portion m mounting surface of the first holding member 80A in advance.

  Alternatively, the radius of curvature of the bent portion m is formed larger than the radius of curvature of the vertical hole portion 10b2, and the bent portion m is inserted into the vertical hole portion 10b2 in a contracted state. It is also possible to use an attachment. In any case, the permanent magnet Z is attached to the second blade chamber 10b by the first holding member 80A.

  The first holding 80A is obtained by sheet metal press molding, and can be manufactured at high cost while being highly accurate. The permanent magnet can be easily attached to the blade chamber 10b by inserting the permanent magnet into the blade chamber 10b after being attached to the holding member 80A.

  Since the protrusion (bending) height of the holding protrusion h constituting the first holding member 80A is made larger than the thickness of the permanent magnet Z, the impact in a state where the permanent magnet Z magnetically attracts the blade 11b. 80A receives the holding member. Therefore, the permanent magnet Z can be prevented from being damaged, and the reliability can be improved.

Next, the second holding member 80B shown in FIG. 17B will be described.
The second holding member 80B is curved so as to be along a part of the peripheral surface of the second blade chamber 10b, and a holding projection n is integrally provided on this one surface. The axial length of the second blade chamber 10b matches the length of the second holding member 80B.

  In order to attach the second holding member 80B to the second blade chamber 10b, the permanent magnet Z is attached to the second holding member 80B in advance and then inserted into the blade chamber 10b. An adhesive may be applied to the holding member 80B, or the radius of curvature of the holding member 80B may be larger than the radius of curvature of the blade chamber 10b and inserted in a contracted state, and the repulsive force may be applied to the blade chamber 10b.

The protrusion height of the holding protrusion m is slightly higher than the plate thickness of the permanent magnet Z, and the blade 11b does not contact the permanent magnet Z when the blade 11b is magnetically attracted. Therefore, the permanent magnet Z can be prevented from being damaged, and the reliability can be improved.
Since the permanent magnet Z directly faces the blade 11b, the magnetic force of the permanent magnet Z acts on the blade 11b with certainty, thereby improving the reliability.

In the embodiment described above, the half capacity operation that is half of the full capacity is performed in which the cylinder resting operation is performed in one cylinder chamber in contrast to the full capacity operation in which the compression operation is performed in both cylinder chambers in the normal operation. However, the present invention is not limited to this.
That is, it is possible to switch between full capacity operation and operation with an arbitrary compression capacity by appropriately changing the displacement volume of the cylinder chamber on the side where cylinder resting is performed.

  Furthermore, the present invention is not limited to the above-described embodiments as they are, and can be embodied by modifying the constituent elements without departing from the scope of the invention in the implementation stage. Various inventions can be formed by appropriately combining a plurality of constituent elements disclosed in the above-described embodiments.

  DESCRIPTION OF SYMBOLS 1 ... Sealed container, 4 ... Electric motor part, 3A ... 1st compression mechanism part, 3B ... 2nd compression mechanism part, 2, 2A ... Intermediate partition plate, Sa ... 1st cylinder chamber, Sb ... 2nd cylinder Chamber, 10a ... first blade chamber, 10b ... second blade chamber, 6A ... first cylinder, 6B ... second cylinder, a ... first eccentric portion, b ... second eccentric portion, 5 ... Rotating shaft, 9a ... first eccentric roller, 9b ... second eccentric roller, 11a ... first blade, 11b ... second blade, 14 ... spring member, K ... pressure switching valve, 25 ... slider hole, DESCRIPTION OF SYMBOLS 21 ... Valve body, 24 ... Slider, 27 ... Blade chamber communication path, 26 ... Suction communication path, 28 ... Discharge communication path, 30 ... Notch part, 60 ... Step part (positioning means), 12 ... Valve cover (positioning means) ), 25C ... Slider hole (positioning means), 15 ... Oil sump , 23 ... Magnetic member, 22 ... Electromagnetic coil, 31 ... Cylindrical member, 70 ... Guide pipe, 73 ... Side hole, Z ... Permanent magnet, R ... Sealed compressor, 17 ... Condenser, 18 ... Expansion device, 19 ... Evaporator.

Claims (9)

The motor part and the compression mechanism part are accommodated in the sealed container,
The compression mechanism is
A first cylinder and a second cylinder provided with an intermediate partition plate, each having a cylinder chamber formed in an inner diameter portion thereof, and a blade chamber communicating with each cylinder chamber;
A rotating shaft that is housed in each of the cylinder chambers of the first cylinder and the second cylinder, has a first eccentric portion and a second eccentric portion, and is connected to the electric motor portion;
A first eccentric roller and a second eccentric roller fitted to the first eccentric portion and the second eccentric portion of the rotating shaft,
A first blade and a second blade, which are movably accommodated in the blade chamber, and abut against each of the first eccentric roller and the second eccentric roller to define a cylinder chamber;
Only the first cylinder is provided with a spring member for applying an elastic force to the first blade,
The second blade is pressed and urged to come into contact with the second eccentric roller by the discharge pressure guided to the second blade chamber, and the second blade by the suction pressure guided to the second blade chamber. Is held away from the eccentric roller of
The closed container contains at least a part of a pressure switching valve for switching the pressure of the second blade chamber provided in the second cylinder to the discharge pressure and the suction pressure,
The pressure switching valve has a valve body having a slider hole, and a slider disposed in the slider hole of the valve body,
A blade chamber communication path communicating with the second blade chamber, a suction communication path communicating with the suction side of the second cylinder chamber, and a discharge communicating with the inside of the sealed container, through the slider hole of the pressure switching valve The communication path is connected,
A notch portion is provided on a part of the peripheral surface of the slider so that the suction communication path or the discharge communication path communicates with the blade chamber communication path according to the position of the slider.
The slider
A first operating position communicating the second blade chamber and the space in the sealed container;
A hermetic compressor, wherein the second blade chamber can be switched to a second operating position that communicates the suction side of the second cylinder chamber. 2. The hermetic seal according to claim 1 , wherein the pressure switching valve is provided with slider positioning means so that the slider of the pressure switching valve is restrained at a position where the blade chamber communication passage and the suction communication passage communicate with each other. Mold compressor. An oil reservoir for collecting lubricating oil is provided at the bottom of the sealed container,
2. The hermetic compressor according to claim 1, wherein the pressure switching valve is immersed in the lubricating oil in the oil reservoir. The pressure switching valve
The slider is reciprocally driven by a combination of a magnetic member integrally formed with the slider or coupled to the slider and an electromagnetic coil provided on the peripheral surface of the magnetic member,
Between the magnetic member and the solenoid valve, a cylindrical member having one end closed and the other end opened is interposed through the sealed container,
The open end of the cylindrical member is fixed to the valve body, the closed end of the cylindrical member protrudes outside the sealed container, and the electromagnetic coil is attached to the outer peripheral surface of the closed end of the cylindrical member. The hermetic compressor as described. 5. The hermetic compressor according to claim 4 , wherein the cylindrical member is bonded to a guide pipe provided in the hermetic container by high frequency induction heating. 2. The hermetic compressor according to claim 1, wherein the valve main body of the pressure switching valve is also used as the intermediate partition plate. Provided in the pressure switching valve, the communication passage suction communicates with the second blade chamber and a second cylinder chamber, claim, characterized by being formed by transverse holes provided in the intermediate partition plate 6 The hermetic compressor as described. 2. The hermetic compressor according to claim 1, wherein the blade chamber includes a permanent magnet that holds the blade away from the roller when the compression operation is stopped. A refrigeration cycle apparatus comprising the hermetic compressor according to any one of claims 1 to 8 , a condenser, an expansion device, and an evaporator to constitute a refrigeration cycle.

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