WO2010024409A1

WO2010024409A1 - Enclosed compressor, two-cylinder rotary compressor, and refrigerating cycle apparatus

Info

Publication number: WO2010024409A1
Application number: PCT/JP2009/065114
Authority: WO
Inventors: 俊彦二見; 卓也平山
Original assignee: 東芝キヤリア株式会社
Priority date: 2008-08-29
Filing date: 2009-08-28
Publication date: 2010-03-04

Abstract

In an enclosed container (1), there is mounted a portion of a pressure switching valve (K) for switching the pressure of a second blade chamber (10b) formed in a second cylinder (6B), into a discharge pressure and a suction pressure. The pressure switching valve (K) is equipped with a valve body (21) having a slider hole (25) along the axial direction, and a slider (24) arranged in the slider hole (25). The slider (24) can be switched between a first operation position, at which the spaces in the second blade chamber (10b) and the enclosed container (1) communicate with each other, and a second operation position, at which the second blade chamber (10b) and a suction communication passage (26) to be connected with a second cylinder chamber (Sb) communicate with each other, so that the capacities of the full-capacity run and the half-capacity run can be varied. Thus, the constitution is simplified, and the number of parts is decreased to reduce the step number. The influences on the cost can be suppressed to shorten the time period the run-switching.

Description

Hermetic compressor, two-cylinder rotary compressor, and refrigeration cycle apparatus

The present invention relates to a hermetic compressor capable of switching compression capacity, a two-cylinder rotary compressor capable of switching between full capacity operation and half capacity operation, and a refrigeration cycle comprising these compressors. The present invention relates to a refrigeration cycle apparatus.

(Closed compressor)
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, a pipe that branches from a suction pipe that communicates the accumulator and the second cylinder chamber is provided, and a pipe that communicates with the branch chamber and a blade chamber provided in the second cylinder and communicates with the inner bottom of the sealed container. An invention has been disclosed in which a first open / close valve is provided in a branch pipe, and a second open / close valve is provided in a pipe communicating with the inner bottom of a sealed container (Japanese Patent Laid-Open No. 2006-300140).

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.

Further, an invention is disclosed in which a blade chamber is partitioned by a cylinder and a sealed container, and a slider is reciprocated by an electromagnetic coil to open and close a suction passage that communicates the suction pipe and the blade chamber (Japanese Patent Laid-Open No. 5-256286). ).

¡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 opposite direction and the suction passage is closed, the discharge pressure gas 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.

(2-cylinder rotary compressor)
A two-cylinder rotary 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 variable capacity operation can be performed 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, two cylinder chambers are provided, each of the cylinder chambers includes a roller that rotates eccentrically, and a compression mechanism that includes a blade that elastically contacts the roller, and the blade of one cylinder chamber is held away from the roller. A two-cylinder rotary compressor having a high-pressure introducing means for increasing the pressure in the cylinder chamber and interrupting the compression action has been disclosed (Japanese Patent Laid-Open No. 1-2247786).

A vane that bisects the cylinder chamber of the first cylinder and the second cylinder is accommodated in the vane chamber, the vane on the first cylinder side is pressed and urged by a spring member, and the vane on the second cylinder side is moved to the vane chamber. A rotary-type hermetic compressor is disclosed that is pressed and urged by a differential pressure between a guided internal pressure of the case and a suction pressure or a discharge pressure guided to a cylinder chamber (Japanese Patent Laid-Open No. 2004-301114).

(Closed compressor)
However, in the hermetic compressor disclosed in Japanese Patent Application Laid-Open No. 2006-300440, a branch pipe branched from the suction pipe, a pipe communicating with the bottom of the sealed container, a pipe communicating with the blade chamber, and two open / close Valves must be arranged, and a member for partitioning the blade chamber into a closed space is also required, which increases the number of parts and increases the part cost.

Of course, a lot of man-hours are required for mounting and assembling each part, which adversely affects the 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 the hermetic compressor disclosed in Japanese Patent Application Laid-Open No. 5-256286, the discharge gas is configured to be guided to the blade chamber through the gap between the cylinder and the hermetic container. take time. 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.

¡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.

(2-cylinder rotary compressor)
In the two-cylinder rotary type compressor capable of switching between the full capacity operation and the half capacity operation as described above, the motor efficiency of the electric motor section decreases as the rotational speed decreases. Therefore, it is necessary to improve motor efficiency by doubling the number of rotations of the rotating shaft in the low capacity range where the capacity is reduced by half.

In the above-mentioned compressor, since the portion with the largest shaft sliding loss is the eccentric portion of the rotating shaft, the sliding loss at this eccentric portion must be reduced. However, in the compressors described in JP-A-1-247786 and JP-A-2004-301114, as the rotational speed is increased, the shaft sliding loss ratio increases, and the capacity is reduced by half. It is difficult to improve motor efficiency.

The rotating shaft has a main shaft portion that is supported by the main bearing and a sub shaft portion that is supported by the sub bearing. However, when the eccentric roller is incorporated in the eccentric portion of the rotating shaft, the axial length is reduced. If the eccentric roller is inserted from the side of the sub shaft shorter than the main shaft, the operation can be easily performed. Therefore, in order to make the insertion of the eccentric roller easier, it is conceivable to simply set the shaft diameter of the auxiliary shaft portion to be small.

However, on the other hand, if the shaft diameter of the auxiliary shaft portion is simply set small, the surface pressure of the shaft surface of the auxiliary shaft portion is likely to increase during the actual compression operation. In particular, it becomes difficult to form an oil film of a lubricating oil in a low rotation range (low performance range), leading to a decrease in reliability.

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.

The 2-cylinder type is a two-cylinder engine that ensures the improvement of motor efficiency during half-capacity operation while ensuring reliability, assuming that the capacity can be varied between full-capacity operation and half-capacity operation. It is an object of the present invention to provide a rotary compressor and a refrigeration cycle apparatus provided with the two-cylinder rotary compressor and capable of improving the refrigeration cycle efficiency.

In order to satisfy the above object, the hermetic compressor of the present invention accommodates an electric motor part and a compression mechanism part in a hermetic container, and the compression mechanism part interposes an intermediate partition plate and the first cylinder and the second cylinder. A cylinder chamber was formed in each inner diameter portion, and a blade chamber communicating with each cylinder chamber was provided.

In order to satisfy the above object, a two-cylinder rotary compressor of the present invention houses an electric motor part and a compression mechanism part in a hermetic container, and the compression mechanism part has an inner diameter part with an intermediate partition plate interposed therebetween. The first cylinder and the second cylinder are provided, and the main bearing that forms the first cylinder chamber is formed on the motor part side of the first cylinder so as to cover the intermediate partition plate and the inner diameter part of the first cylinder, A secondary bearing that forms a second cylinder chamber covering the inner partition plate and the inner diameter portion of the second cylinder is mounted on the side opposite to the motor portion of the cylinder, and the rotary shaft connected to the motor portion is connected to the first cylinder chamber and the first cylinder chamber. The two cylinder chambers have two eccentric portions whose rotational angles are shifted from each other by 180 °, a main shaft portion pivotally supported by the main bearing, and a subshaft portion pivotally supported by the sub-bearing. The first cylinder chamber and the second cylinder chamber are fitted with an eccentric roller in the part. A rotation mechanism that is rotationally driven and enables switching between compression operation and non-compression operation in the second cylinder chamber, and the sub-shaft portion shaft diameter φDb of the rotary shaft that is pivotally supported by the sub-bearing is expressed by equation (1) It is configured to hold.

ΦDa: Shaft diameter of the main shaft of the rotary shaft supported by the main bearing. L1: An axial distance from the axial center position of the first cylinder to the axial load position of the rotary shaft main shaft portion (distance half the main shaft portion shaft diameter from the first cylinder chamber side end portion of the main shaft portion). L2: An axial distance from the axial center position of the first cylinder to the axial center position of the second cylinder. L3: Axial distance from the axial center position of the second cylinder to the axial load position of the rotary shaft countershaft portion (distance from the second cylinder chamber side end of the subshaft portion to a half of the shaft diameter of the subshaft portion) . L4: sliding length between the eccentric portion of the rotating shaft and the eccentric roller. E: The amount of eccentricity of the eccentric part of the rotating shaft.

It is explanatory drawing which shows the refrigeration cycle structure of the refrigeration cycle apparatus of the vertical cross section which a part of the hermetic compressor provided with the pressure switching valve according to the first embodiment of the present invention is omitted. It is a cross-sectional plan view of the same hermetic compressor. It is a front view which shows the same pressure switching valve. It is a top view which shows the same pressure switching valve. It is a top view which shows another state of the same pressure switching valve. It is sectional drawing which abbreviate | omitted one part of the hermetic compressor provided with the pressure switching valve which concerns on 2nd Embodiment in this invention. It is a longitudinal cross-sectional view which expands a principal part and shows the state at the time of full capacity driving | operation of the hermetic compressor which concerns on the said 2nd Embodiment. It is a longitudinal cross-sectional view which expands a principal part and shows the state at the time of half capacity operation of the hermetic compressor. It is a cross-sectional top view of the principal part of the hermetic compressor which concerns on 3rd Embodiment in this invention. It is a longitudinal cross-sectional view of the principal part of the hermetic compressor which concerns on 4th Embodiment in this invention. It is a top view of the pressure switching valve concerning a 5th embodiment in the present invention. FIG. 9B is a longitudinal sectional view of the same pressure switching valve taken along line BB in FIG. 9A and viewed in the direction of the arrow. It is a longitudinal cross-sectional view which shows the state of the pressure switching valve at the time of full capacity driving | operation of the hermetic compressor which concerns on 6th Embodiment in this invention. It is a longitudinal cross-sectional view which shows the state of the pressure switching valve at the time of the half capacity | capacitance driving | running of the hermetic compressor. It is a longitudinal cross-sectional view which shows the state of the pressure switching valve at the time of full capacity driving | operation in the modification of the same hermetic compressor. It is a longitudinal cross-sectional view which shows the state of the pressure switching valve at the time of full capacity operation in the further different modification of the hermetic compressor. It is a longitudinal cross-sectional view which shows the state of the pressure switching valve at the time of the capability half operation of the hermetic compressor which concerns on 7th Embodiment in this invention. It is a cross-sectional top view which shows the state of the pressure switching valve at the time of the half capacity | capacitance driving | operation of the hermetic compressor. It is a longitudinal cross-sectional view which shows the state of the pressure switching valve at the time of full capacity driving | operation of the hermetic compressor which concerns on 7th Embodiment in this invention. It is a cross-sectional top view which shows the state of the pressure switching valve at the time of full capacity driving | operation of the hermetic compressor. It is a 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 a half capacity operation according to the modification in the seventh embodiment. It is a top view of a part of cylinder which shows the attachment structure of the permanent magnet which concerns on 8th Embodiment in this invention. It is a top view which shows a cylinder part in the attachment structure by the 1st holding member holding the same permanent magnet. It is a top view which shows the 2nd holding member in the attachment structure by the 1st holding member holding the same permanent magnet. It is a perspective view which shows the 1st holding member which concerns on the modification in the 8th Embodiment. It is a front view which shows the 1st holding member. It is a side view which shows the 1st holding member. It is explanatory drawing which shows the schematic longitudinal cross-section of the 2-cylinder rotary compressor which concerns on 9th Embodiment in this invention, and the refrigerating-cycle structure of a refrigerating-cycle apparatus. It is a longitudinal cross-sectional view which expands and shows the principal part of the same 2-cylinder rotary compressor. It is a partially exploded perspective view which shows the principal part of the 2 cylinder rotary compressor. It is a characteristic figure of the eccentric part sliding loss with respect to the eccentric part sliding length / eccentric part axial diameter in the same 2-cylinder rotary compressor. It is a characteristic figure of the total efficiency with respect to the eccentric part sliding length / eccentric part axial diameter in the same 2-cylinder rotary compressor.

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.

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 A and the second compression mechanism unit 3 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 Xa and a second eccentric portion Xb that penetrate the

cylinders

6A and 6B and have a phase difference of about 180 °.

Each eccentric part Xa, Xb has the same diameter as each other, and is assembled so as to be positioned at the inner diameter part of each

cylinder

6A, 6B. The first eccentric roller 9a is fitted to the peripheral surface of the first eccentric portion Xa, and the second eccentric roller 9b is fitted to the peripheral surface of the second eccentric portion Xb.

The first cylinder chamber Sa is formed in the inner diameter portion of the first cylinder 6A, and the 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.

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 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 hermetic compressor R, the condenser 17, the expansion device 18, the evaporator 19, and the accumulator 20 described above are sequentially connected by piping to constitute a refrigeration cycle apparatus.

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. 3A is a schematic front view of the pressure switching valve K. FIG. 3B and 3C 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, 3B and 3C, the valve body 21 has an inner portion and an outer portion curved, and in the front view shown in FIG. 3A, the upper end surface and the lower end surface are formed flat. The substantially prismatic 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.

The suction communication passage 26, the blade chamber communication passage 27, and the discharge communication passage 28, each of which is a predetermined distance from one end face of the valve body 21, are provided apart 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 as a reference. 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 the slider hole 25 provided in the valve body 21 and the 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. And it is displaced to a position facing 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 turned off, the magnetic attraction to 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 30 faces the blade chamber communication passage 27 and the suction communication passage 26 as shown in FIG. 3C. 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. .

Further, the blade chamber communication passage 27 is opened to the second blade chamber 10b, 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 path 27 and the discharge communication path 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 driven to rotate, so that the first and second

eccentric rollers

9a and 9b rotate eccentrically in the respective 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 and is 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 led 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 compression action exactly the same as that of the first cylinder chamber Sa is also performed 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 of the second blade 11b is under a suction pressure (low pressure), while the front end is in a low pressure atmosphere by a 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.

Thus, 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 is not required, 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.

Furthermore, in order to attach the pressure switching valve K to the second cylinder 6B, it is only necessary to provide a screw hole for the 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 larger than the diameter of the suction communication passage 26. Formed.

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 passage 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.

The oil reservoir 15 for collecting the lubricating oil is provided at the bottom of the sealed container 1 so that 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 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 the main part of the hermetic compressor R provided with the 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 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 sealed container 1 and the circumferential surface of the cylindrical member 31 inserted therethrough are brazed using a brazing material (seal material) (see V in the figure), and are completely sealed. ing. The closed end surface of the cylindrical member 31 protrudes to the outside of the sealed container 1, and the electromagnetic coil 22 A is fitted and fixed to the outer peripheral surface of the end portion.

Furthermore, 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 23A 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 Xd formed in a small diameter having 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 main body 21A. Have. A sliding contact portion Xe is integrally connected to both ends of the notch portion 30A at the front end of the flange portion Xd with the notch portion 30A interposed therebetween.

The sliding contact portion Xe is slidably fitted in the slider hole 25A. The notch 30A is designed to have a diameter smaller than the diameter of the slider hole 25A and substantially the same diameter as the flange Xd. Therefore, a narrow gap is formed between the peripheral surface of the cutout portion 30A and the peripheral surface of the slider hole 25A, and between the peripheral surface of the flange portion Xd 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”.

When the electromagnetic coil 22B is de-energized, the magnetic attractive 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.

This closes the discharge communication path 28A, which is an opening formed in the end face of the valve body 21A. 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.

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 end 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 compression action exactly the same as that of the first cylinder chamber Sa is also performed 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 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.

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. Therefore, there is no differential pressure at the front and rear end portions 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 the electromagnetic coil 22A need not be immersed in the lubricating oil in the oil reservoir 15, the electromagnetic coil 22A need not have 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 path (not shown) communicating with the second blade chamber 10b, a suction communication path 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 is exposed to the discharge pressure, so some kind of closing member is necessary.

With the above configuration, the intermediate partition plate 2 also serves as a valve body originally provided in the pressure switching valve Ka. 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 with a predetermined distance from each other and extending from the same side surface to 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.

If the pressure switching valve Ka has such a configuration, the protrusion amount of the actuator 50 from the valve body 21D can be minimized. 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 embodiment, the slider 24 is displaced to the “second operating position” in order to perform the cylinder resting operation (capacity half operation). 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 the pressure switching valve Kb and a part of the hermetic compressor provided with the pressure switching valve Kb in the sixth embodiment. FIG. 10A shows a state during full capacity operation, and FIG. 10B shows a state during half capacity operation.

The basic configuration of the pressure switching valve Ka 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 controlled to be switched according to 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 reverse 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 main 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 passage 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 24A is provided with a through hole 61 at the center axis position along the axial direction, and both ends of the slider 24A 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, so 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 surface of the slider 24A is retracted to a position where the blade chamber communication passage 27A of the valve body 21A is opened, and is in a “first operation position” where the blade chamber communication passage 27A communicates with the discharge communication passage 28A. Displace. 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. 10B, 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, which 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 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 the other configuration is the same as that shown in FIGS. 10A and 10B, the same number is assigned and a new description is omitted.

During cylinder resting operation, the polarity of the electromagnetic coil 22B is switched to the opposite polarity, so that the slider 24A moves leftward from the state shown in the figure, 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.

Thus, instead of providing the slider body positioning means in the valve main body 21C, the valve cover 12 which is an existing part can also be used, 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.

Furthermore, a suction communication path 26A, a blade chamber communication path 27A, and a discharge communication path 28A are provided in an extension of the auxiliary bearing 8A.

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 are not changed. Since the other configuration is the same as that shown in FIGS. 10A and 10B, the same number is assigned and a new description is 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 auxiliary bearing 8A which is an existing part, and the influence on the cost is suppressed. 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 including 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. 13A, 13B, 14A, and 14B are a schematic longitudinal sectional view of a part of a hermetic compressor including the pressure switching valve Ke and the pressure switching valve Ke according to the seventh embodiment, and a schematic view. FIG.

FIGS. 13A and 13B show a state during half-capacity operation, and FIGS. 14A and 14B show a state during 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 which 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 the hole through which the rotation shaft is inserted, and the slider 24A is inserted. 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.

As compared with the case where the cylindrical member 31 is brazed 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 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.

It should be noted that the intermediate partition plate 2 A portion of the lateral hole 73 is closed with 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 that connects the slider hole 25 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 that communicates the hole 25 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 and the blade chamber are provided via the notch 30A of the slider 24A and the slider hole 25D. The communication path 27B communicates. 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.

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 shows a modification of the seventh embodiment. Only the configuration different from 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 smaller than that of the sealed container 1 (material or form having low rigidity) is selected. An auxiliary pipe 73 is fixed to the cylindrical member 31, and the auxiliary pipe 73 is made of a material having a Young's modulus smaller than that of the cylindrical member 31 (a material or a form having low rigidity).

The cylindrical member 31 is attached to the sealed container 1 by joining and fixing the guide pipe 70 and the auxiliary pipe 73 by brazing.

That is, the guide pipe 70 and the auxiliary pipe 73 are heated during the brazing process, but these are made of a material having low rigidity, and can prevent the cylindrical member 31 attached to the sealed container 1 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 73 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 73 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, the blade during the idle cylinder operation that stops the compression action does not act on the blade due to the differential pressure between the discharge pressure and the suction pressure, 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, the permanent magnet mounting structure in the blade chamber is improved in consideration of the above problems.

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, the 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 a 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 rear end of the second blade 11b is formed to have a length that adheres to the permanent magnet Z when the front end is in a position where it is slightly recessed 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 attracting 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.

Since it is not necessary to process the cylinder 6B and the blade chamber 10b in order to attach the permanent magnet Z, 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 modified examples 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 that holds the second blade 11b in the second blade chamber 10b. It is a top view of holding member 80B.

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 H-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, and a lower horizontal piece. A base portion Xg provided with a piece projecting downward from the center of the piece, a bent portion Xm integrally bent from both ends of the horizontal piece of the base portion Xg, and a holding projection Xh described later provided on the base portion Xg It consists of.

The holding protrusion Xh has a pair of protrusions that are cut in a direction opposite to the bending direction of the bending portion Xm, with a predetermined interval in the vertical direction at the center of the vertical piece of the base portion Xg, and the protrusion It is composed of bent pieces that are bent in opposite directions to the bending direction of the bent portion Xm along the both side edges of the base portion Xg at portions facing each other. The protrusion (folding) height of the holding projection Xh is made 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 Xh and the bent piece. In order to ensure reliability, it is preferable to apply an adhesive between the holding projection Xh 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 Xm mounting surface of the first holding member 80A in advance.

Alternatively, the radius of curvature of the bent portion Xm is formed larger than the radius of curvature of the vertical hole portion 10b2, and the bent portion Xm is inserted into the vertical hole portion 10b2 in a contracted state, and the elastic repulsive force of the bent portion Xm. 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 press forming a sheet metal and can be manufactured at a low 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 Xh constituting the first holding member 80A is made larger than the thickness of the permanent magnet Z, the impact when the permanent magnet Z magnetically attracts the blade 11b. 80A receives the holding member. Therefore, damage to the permanent magnet Z can be prevented, and 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 Xn is integrally provided on the 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 Xm 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.

FIG. 19 is a longitudinal sectional view of a two-cylinder rotary compressor Q and a diagram showing a refrigeration cycle configuration of a refrigeration cycle apparatus. FIG. 20 is an enlarged longitudinal section of the main part of the two-cylinder rotary compressor Q. FIG. 21 is an exploded perspective view of a part of the two-cylinder rotary compressor Q. (In order to avoid complications in the drawings, there are parts that are not denoted by reference numerals even if they are explained, and there are parts that are not explained even if they are shown. The same applies hereinafter).
First, the two-cylinder rotary compressor Q will be described. 101 is a hermetic container, and a compression mechanism 103 is provided in the lower part of the hermetic container 101, and an electric motor part 104 is provided in the upper part. The compression mechanism unit 103 and the electric motor unit 104 are connected by a rotating shaft 105.

The compression mechanism section 103 includes a first cylinder 106A on the upper surface portion of the intermediate partition plate 102 and a second cylinder 106B on the lower surface portion via the intermediate partition plate 102. Further, the main bearing 7 is attached and fixed to the upper surface portion of the first cylinder 106A, and the auxiliary bearing 108 is attached and fixed to the lower surface portion of the second cylinder 106B.

The main bearing 107 supports the main shaft portion 105 a of the rotating shaft 105, and the auxiliary bearing 108 supports the auxiliary shaft portion 105 b of the rotating shaft 105. Further, the rotating shaft 105 penetrates through the first and

second cylinders

106A and 106B, and integrally forms the first eccentric portion Ya and the second eccentric portion Yb formed with a phase difference of about 180 °. I have.

The first and second eccentric portions Ya and b have the same shaft diameter and are assembled so as to be positioned at the inner diameter portions of the first and

second cylinders

106A and 106B. A first eccentric roller 109a is fitted to the circumferential surface of the first eccentric portion Ya, and a second eccentric roller 109b is fitted to the circumferential surface of the second eccentric portion Yb.

The inner diameter portion of the first cylinder 106A is surrounded by the main bearing 107 and the intermediate partition plate 102 to form a first cylinder chamber Ta. An inner diameter portion of the second cylinder 106B is surrounded by the auxiliary bearing 108 and the intermediate partition plate 102, and a second cylinder chamber Tb is formed.

The cylinder chambers Ta and Tb are formed to have the same shaft diameter and height dimension, and the

eccentric rollers

109a and 109b are partly accommodated so that they can be eccentrically rotated while being in line contact with the peripheral walls of the cylinder chambers Ta and Tb. Is done.

In particular, as shown in FIG. 21, the first cylinder 106A is provided with a first vane chamber 110a communicating with the first cylinder chamber Ta, and the first vane 111a is movably accommodated therein. The second cylinder 106B is provided with a second vane chamber 110b communicating with the second cylinder chamber Tb, and the second vane 111b is movably accommodated therein.

The tip ends of the first and

second vanes

111a and 111b are formed in a semicircular shape in a plan view, and project into the opposing cylinder chambers Ta and Tb and have a circular shape in the plan view. Line contact can be made with the peripheral walls of the

rollers

109a and 109b regardless of the rotation angle.

Only the first cylinder 106A is provided with a lateral hole f that communicates the first vane chamber 110a with the outer peripheral surface of the cylinder 106A, and accommodates a spring member 112 that is a compression spring. The spring member 112 is interposed between the rear end side end face of the first vane 111a and the inner peripheral wall of the sealed container 101, and applies an elastic force (back pressure) to the vane 111a.

The second vane chamber 110b does not contain any members other than the second vane 111b. However, depending on the setting environment of the second vane chamber 110b and the operation of the switching mechanism M as described later. The tip edge of the second vane 111b can come into contact with the peripheral surface of the second eccentric roller 109b.

That is, a part of the outer shape of the second cylinder 106B is exposed in the sealed container 101 from the relationship between the outer dimension of the second cylinder 106B and the outer diameter of the intermediate partition plate 102 and the auxiliary bearing 108. The exposed portion of the hermetic container 101 is designed to correspond to the vane chamber 110b. Therefore, the rear end portions of the vane chamber 110b and the vane 111b directly receive the pressure in the case.

In particular, since the second cylinder 106B and the second vane chamber 110b are structures, there is no influence even if they are subjected to the pressure in the case, but the second vane 111b is slidable in the second vane chamber 110b. And the rear end thereof is located in the second vane chamber 110b, so that the pressure in the sealed container 101 is directly received.

Further, the tip of the second vane 111b faces the second cylinder chamber Tb, and the tip of the vane 111b receives the pressure in the cylinder chamber Tb. Eventually, the second vane 111b is configured to move in a direction from a higher pressure to a lower pressure according to the mutual pressure received by the front end and the rear end.

As shown in FIG. 19 again, the refrigerant pipe G is connected to the upper end of the sealed container 101. The refrigerant pipe G is connected to an accumulator 118 through a condenser 115, an expansion device 116, and an evaporator 117, and is further connected from the accumulator 118 to the two-cylinder rotary compressor Q to constitute a refrigeration cycle.

In other words, two suction refrigerant tubes Ga and Gb are connected to the two-cylinder rotary compressor Q from the bottom of the accumulator 118. One suction refrigerant pipe Ga penetrates the sealed container 101 and the side of the first cylinder 106A, and communicates directly with the first cylinder chamber Ta. The other suction refrigerant pipe Gb passes through the side of the second cylinder 106B via the hermetic container 101, and communicates directly with the second cylinder chamber Tb.

Further, a branch refrigerant pipe Gc is branched from a middle portion of the refrigerant pipe G communicating with the two-cylinder rotary compressor Q and the condenser 115. The branch refrigerant pipe Gc is provided with a first on-off valve 120 in the middle, and is connected to the middle part of the suction refrigerant pipe Gb that communicates the accumulator 118 and the second cylinder chamber Tb.

Furthermore, a second on-off valve 121 is provided upstream of the connection portion of the branch refrigerant pipe Gc in the suction refrigerant pipe Gb. Each of the first on-off valve 120 and the second on-off valve 121 is an electromagnetic on-off valve.

Thus, the switching mechanism M is configured by the suction refrigerant pipe Gb, the branch refrigerant pipe Gc, the first on-off valve 120, and the second on-off valve 121 connected to the second cylinder chamber Tb. In accordance with the switching operation of the switching mechanism M, the suction pressure or the discharge pressure is guided to the cylinder chamber Tb of the second cylinder 106B.

Next, the operation of the refrigeration cycle apparatus provided with the above-described two-cylinder rotary compressor Q will be described.

a) When normal operation (full capacity operation) is selected:
When an instruction for normal operation is entered, the control unit controls the first on-off valve 120 of the switching mechanism M to close and the second on-off valve 121 to open, and also sends an operation signal to the motor unit 104 via the inverter. Send. The rotating shaft 105 is driven to rotate, and the first and second

eccentric rollers

109a and 109b simultaneously perform eccentric rotation in the first and second cylinder chambers Ta and Tb.

In the first cylinder 106A, since the first vane 111a is always elastically pressed and biased by the spring member 112, the leading edge of the first vane 111a is in sliding contact with the peripheral wall of the first eccentric roller 109a. The first cylinder chamber Ta is divided into a suction chamber and a compression chamber.

The position of the inner circumferential surface of the first cylinder chamber Ta where the circumferential surface of the first eccentric roller 109a is in rolling contact with the tip of the first vane 111a is the first cylinder chamber with the first vane 111a retracted most. The space capacity of Ta is maximized. The refrigerant gas is sucked from the accumulator 118 through the refrigerant pipe Ga into the first cylinder chamber Ta to be filled.

Further, along with the eccentric rotation of the first eccentric roller 109a, the rolling contact position with the inner peripheral surface of the first cylinder chamber Ta on the peripheral surface of the first eccentric roller 109a moves, and the first cylinder chamber Ta is partitioned. The volume of the compression chamber is reduced. That is, the gas previously introduced into the first cylinder chamber Ta is gradually compressed.

The rotating shaft 105 is continuously rotated, the capacity of the compression chamber partitioned into the first cylinder chamber Ta is further reduced, the gas is compressed, and the discharge valve is opened when the pressure rises to a predetermined pressure. The high-pressure gas is discharged into the sealed container 101 through the valve cover and is filled. And it discharges from the refrigerant | coolant pipe | tube G connected to the airtight container 101 upper part.

On the other hand, since the first on-off valve 120 constituting the switching mechanism M is closed, the discharge pressure (high pressure) is not guided to the second cylinder chamber Tb. Since the second on-off valve 121 is opened, the low-pressure evaporative refrigerant evaporated by the evaporator 117 and gas-liquid separated by the accumulator 118 is guided to the second cylinder chamber Tb.

The second cylinder chamber Tb is in a suction pressure (low pressure) atmosphere, while the second vane chamber 110b is exposed in the sealed container 101 and is under a discharge pressure (high pressure). In the 2nd vane 111b, the front-end | tip part becomes a low pressure condition, and a rear-end part becomes a high pressure condition, and a differential pressure | voltage exists in a front-and-back end part.

</ RTI> Under the influence of this differential pressure, the tip of the second vane 111b is pressed and urged so as to be in sliding contact with the second eccentric roller 109b. Therefore, the compression action is performed also in the second cylinder chamber Tb, and the full capacity operation is performed in which the compression action is performed in both the first cylinder chamber Ta and the second cylinder chamber Tb.

The high pressure gas discharged from the sealed container 101 through the refrigerant pipe G is condensed and liquefied by exchanging heat with the outside air or water in the condenser 115, adiabatically expanded in the expansion device 116, and evaporated from the heat exchange air in the evaporator 117. Takes out latent heat and freezes.

Then, the evaporated refrigerant is guided to the accumulator 118 and separated into gas and liquid, and again from the suction refrigerant pipes Ga and Gb to the first cylinder chamber Ta and the second cylinder chamber Tb2 in the two-cylinder rotary compressor Q. Inhaled, the above-mentioned action is performed, and the above-mentioned route is circulated.

b) When special operation (capability half operation) is selected:
When the special operation (operation that halves the compression capacity) is selected, the switching mechanism M switches and sets so that the first on-off valve 120 is opened and the second on-off valve 121 is closed. In the first cylinder chamber Ta, the normal compression action is performed as described above, and the high-pressure gas discharged into the hermetic container 101 is filled to become a high pressure in the case.

A part of the high-pressure gas discharged from the refrigerant pipe G is divided into the branch refrigerant pipe Gc and introduced into the second cylinder chamber Tb through the opened first on-off valve 120 and the suction refrigerant pipe Gb. While the second cylinder chamber Tb becomes a discharge pressure (high pressure) atmosphere, the second vane chamber 110b remains in the same situation as the high pressure in the case.

Therefore, the second vane 111b is affected by the high pressure at both the front and rear ends, and there is no differential pressure at the front and rear ends. The second vane 111b is kicked along with the rotation of the eccentric roller 109b, and maintains a stopped state at a position separated from the peripheral surface.

The second eccentric roller 109b remains idling, and no compression action is performed in the second cylinder chamber Tb (non-compression operation state). Eventually, only the compression action in the first cylinder chamber Ta is effective, and an operation with half the capacity is performed.

Note that the switching mechanism M that switches between the compression operation and the non-compression operation in the second cylinder chamber Tb is not limited to that shown in the above embodiment. For example, the pressure in the second vane chamber 110b is switched between high pressure and low pressure, the compression operation is performed in the second cylinder chamber Tb when the pressure in the second vane chamber 110b is high, and the non-compression operation is performed when the pressure is low. May be performed.

Thus, in the two-cylinder rotary compressor Q that enables switching between the compression operation and the non-compression operation in the cylinder chamber on the side of the auxiliary bearing 108, that is, the second cylinder chamber Tb, the auxiliary bearing 108 is pivotally supported. The subshaft portion 105b shaft diameter φDb of the rotating shaft 105 is set so that the following equation (1) is established.

Here, φDa: the diameter of the main shaft portion 105 a of the rotary shaft 105 supported by the main bearing 107.

L1: From the axial center position of the first cylinder 106A to the axial load position of the rotary shaft main shaft portion 105a (the distance Da / 2 from the end of the main shaft portion 105a on the first cylinder chamber Ta side to the half of the main shaft portion 105a shaft diameter φDa). Axial distance to).

L2: An axial distance from the axial center position of the first cylinder 106A to the axial center position of the second cylinder 106B.

L3: The axial load position of the rotary shaft countershaft portion 105b from the axial center position of the second cylinder 106B (the distance half the shaft diameter 105D of the subshaft portion 105b from the end of the subshaft portion 105b on the second cylinder chamber Ta side) Axial distance to Db / 2).

L4: sliding length between the eccentric portion Yb of the rotating shaft 105 and the eccentric roller 109b.

E: Eccentricity of the eccentric part Yb of the rotating shaft 105.

That is, in the above-described two-cylinder rotary compressor Q, the efficiency of the motor that is the motor unit 104 decreases when the rotational speed of the rotary shaft 105 decreases. Therefore, in the low capacity region, the second cylinder chamber Tb is in an uncompressed operation state (hereinafter referred to as “cylinder operation”), and the motor efficiency is controlled to be increased by doubling the rotational speed. .

However, in this case, the shaft sliding loss is increased by increasing the number of revolutions, and in the design specification having a large shaft sliding loss ratio, the motor efficiency cannot be improved by the cylinder resting operation. In particular, in the two-cylinder rotary compressor Q, the portions with the largest shaft sliding loss are the eccentric portions Ya and Yb formed on the rotating shaft 105. Therefore, it is necessary to reduce the sliding loss at these eccentric portions Ya and Yb. There is.

As shown in an enlarged view in FIG. 20, the sliding lengths of the first eccentric portion Ya and the second eccentric portion Yb formed on the rotating shaft 5 with respect to the first eccentric roller 109a and the second eccentric roller 109b. Is L4, and the shaft diameters of the first eccentric portion Ya and the second eccentric portion Yb are φDcr.

FIG. 22 is a characteristic diagram of L4 / φDcr and eccentric part sliding loss when (L4 / φDcr) is taken on the horizontal axis and eccentric part sliding loss [W] is taken on the vertical axis. Comparisons are shown under the same capacity for both hour and idle cylinder operation.

The value of the eccentric portion sliding loss [W] is set such that the sliding length L4 of the first and second eccentric portions Ya and Yb with respect to the first and second

eccentric rollers

109a and 109b is constant, The second eccentric portion shaft diameter φDcr is changed and led. Further, it is assumed that the number of revolutions during the cylinder resting operation is twice that during the two cylinder operation, and the sliding loss of the second eccentric portion Yb that is the cylinder resting side eccentric portion is “0”.

The change during 2-cylinder operation is indicated by a broken line, and the change during idle cylinder operation is indicated by a solid line. From this figure, it can be seen that the loss difference increases as the L4 / φDcr value decreases.

FIG. 23 is a characteristic diagram of L4 / φDcr and total efficiency at the same capacity under the cooling intermediate condition as an air conditioner. Also here, L4 / φDcr is taken on the horizontal axis, the eccentric portion sliding length L4 is constant, and the eccentric portion shaft diameter φDcr is changed. The vertical axis is the overall efficiency.

From this figure, in order to obtain the efficiency improvement due to idle cylinder operation,
L4 / φDcr ≧ 0.43 (2)
It is necessary to satisfy the formula (2).

Measurement conditions for obtaining the above-mentioned cooling intermediate conditions are shown below.

In Table 1, kPaA is an absolute pressure.

As shown in FIG. 20 again, the first eccentric portion Ya has the first eccentric portion Ya between the shaft diameter φDcr of the first and second eccentric portions Ya and Yb and the shaft diameter φDb of the auxiliary shaft portion 105b. In order to incorporate the eccentric roller 109a from the auxiliary shaft portion 105b side
φDcr ≧ φDb + 2 × E (3)
It is necessary to satisfy the formula (3).

Therefore, as a condition for expanding the expressions (2) and (3) and obtaining the efficiency improvement by the idle cylinder operation,
φDb ≦ L4 / 0.43-2 × E (4)
(4) Formula must be satisfied.

On the other hand, as the shaft diameter φDb of the auxiliary shaft portion 105b is reduced, the surface pressure with respect to the shaft surface increases, and it becomes difficult to form an oil film of a lubricating oil particularly in a low rotation region (low performance region), and the reliability deteriorates. .

In the above-described two-cylinder rotary compressor Q, in order to rest the second cylinder chamber Tb on the side of the auxiliary shaft portion 105b in the low capacity region, the gas load Fa applied to the main shaft portion 105a of the rotating shaft 105, The ratio with the gas load Fb applied to the shaft portion 105b is as shown in FIG.
Fa: Fb = (L2 + L3): 1: (5)
It becomes.

Further, the ratio of the surface pressure Na to the main shaft portion 105a and the surface pressure Nb to the sub shaft portion 105b is such that the sliding length ratio under load is equal to the shaft diameter ratio.
Na: Nb = (L2 + L3) / φDa2: L1 / φDb2 (6)
It becomes.

Here, in order to ensure a surface pressure equal to or higher than that of the main shaft portion 105a in the sub shaft portion 105b of the rotating shaft 105,

It is necessary to satisfy the formula (7).

So from these things

Equation (1) is derived.

That is, by satisfying the above-described expression (1), it is possible to sufficiently improve the efficiency by the idle cylinder operation while ensuring the reliability.

What is shown below is a design example that specifically expresses the expression (1).

And the refrigeration cycle apparatus which comprises such a two-cylinder rotary compressor Q and constitutes a refrigeration cycle can further improve the refrigeration efficiency.

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.

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 2-cylinder type is a two-cylinder engine that ensures the improvement of motor efficiency during half-capacity operation while ensuring reliability, assuming that the capacity can be varied between full-capacity operation and half-capacity operation. It is possible to provide a rotary compressor and a refrigeration cycle apparatus that includes this two-cylinder rotary compressor and can improve the efficiency of the refrigeration cycle.

Claims

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;
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
In the closed container, 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 is incorporated,
The pressure switching valve has a valve body having a slider hole, and a slider disposed in the slider hole of the valve body,
The slider
A first operating position communicating the second blade chamber and the space in the sealed container;
A hermetic compressor characterized in that it can be switched to a second operating position that communicates the second blade chamber and the suction side of the second cylinder chamber.
In the slider hole of the pressure switching valve,
A blade chamber communication passage communicating with the second blade chamber;
A suction communication path communicating with the suction side of the second cylinder chamber and a discharge communication path communicating with the inside of the sealed container are connected;
2. A hermetic seal according to claim 1, wherein a notch portion 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. Mold compressor.
3. The hermetic seal according to claim 2, 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.
6. The hermetic compressor according to claim 5, 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.
8. The suction communication passage provided in the pressure switching valve and communicating between the second blade chamber and the second cylinder chamber is formed by a lateral hole provided in the intermediate partition plate. 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 9, a condenser, an expansion device, and an evaporator to constitute a refrigeration cycle.
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 each provided with an intermediate partition plate, each having an inner diameter;
A main bearing attached to the motor part side of the first cylinder and covering the inner diameter part of the first cylinder together with the intermediate partition plate to form a first cylinder chamber;
A sub-bearing attached to the anti-motor part side of the second cylinder and covering the inner diameter part of the second cylinder together with the intermediate partition plate to form a second cylinder chamber;
Two eccentric portions housed in the first cylinder chamber and the second cylinder chamber, respectively, whose rotation angles are shifted from each other by 180 °, a main shaft portion that is supported by the main bearing, and a sub-bearing. A rotating shaft connected to the electric motor part,
An eccentric roller fitted into each of the eccentric portions of the rotating shaft and driven to rotate in the first cylinder chamber and the second cylinder chamber;
A switching mechanism for switching between compression operation and non-compression operation in the second cylinder chamber;
A two-cylinder rotary compressor comprising:
The shaft diameter φDb of the auxiliary shaft portion of the rotary shaft supported by the auxiliary bearing is:

φDa: shaft diameter of the main shaft portion of the rotating shaft supported by the main bearing L1: axial load position of the rotating shaft main shaft portion from the axial center position of the first cylinder (from the first cylinder chamber side end of the main shaft portion to the main shaft L2: Axial distance from the axial center position of the first cylinder to the axial center position of the second cylinder L3: Axial center position of the second cylinder Axial distance from the shaft load position of the rotating shaft subshaft portion (distance from the second cylinder chamber side end of the subshaft portion to half the shaft diameter of the subshaft portion) L4: Eccentric portion and eccentric roller of the rotating shaft Sliding length E: Eccentric amount of the eccentric portion of the rotating shaft A two-cylinder rotary compressor characterized in that the above formula (1) is established.
A refrigeration cycle apparatus comprising the two-cylinder rotary compressor according to claim 11, a condenser, an expansion device, and an evaporator to constitute a refrigeration cycle.