JP6988846B2 - Oil return device - Google Patents

Description

The present invention relates to an oil return device that returns oil to a compressor of a refrigeration cycle device.

Assuming that an oil return device was used, the accumulator connected to the refrigerant suction side of the compressor of the refrigeration cycle device and the oil contained in the refrigerant discharged from the compressor are separated, and the separated oil is returned to the compressor. There are oil separators and the like (see, for example, Patent Document 1).

Japanese Unexamined Patent Publication No. 2013-108710

In conventional accumulators, oil separators, etc., the opening degree of the oil flow path through which oil flows toward the sliding portion of the compressor is fixed. That is, the cross-sectional area of the oil flow path does not change. Therefore, it is not possible to adjust the oil return amount, which is the flow rate of the oil returned to the sliding portion of the compressor.

As a countermeasure, it is conceivable to install a valve mechanism that adjusts the flow rate of oil flowing through the oil flow path. Examples of the valve mechanism include a solenoid valve. However, the physique of the conventional solenoid valve is large. Therefore, if the oil return device is provided with a solenoid valve, the physique of the oil return device increases.

In view of the above points, it is an object of the present invention to provide an oil return device capable of adjusting the amount of oil return while suppressing an increase in the physique of the oil return device.

In order to achieve the above object , according to the inventions of claims 1 and 2 , the oil return device for returning oil to the compressor of the refrigeration cycle device is a device.
Oil flow paths (110, 112, 113, 115, XV1, XV2, 234c, 234d, 241 and 242, 243) through which oil flows from the oil storage chambers (101a, 205) toward the sliding portion of the compressor. The flow path forming portions (103a, 105a, 111, 234a, 234b, 240, X2) to be formed, and
Provided in the flow path forming unit, based on the number of revolutions of the compressors, and a valve component for regulating the flow rate of the oil flowing through the oil flow path (X1).

Valve parts
A base (X11, X121, X13) in which an oil chamber (X19) through which oil flows, a first oil hole (X16) communicating with the oil chamber, and a second oil hole (X17) communicating with the oil chamber are formed.
The drive unit (X123, X124, X125) that displaces when its own temperature changes,
Amplifying units (X126, X127) that amplify the displacement due to changes in the temperature of the driving unit,
By transmitting the displacement amplified by the amplification unit and moving in the oil chamber, it has a movable portion (X128) that switches between communication and shutoff between the first oil hole and the second oil hole via the oil chamber. death,
When the drive unit is displaced due to a change in temperature, the drive unit urges the amplification unit at the urging position (XP2), so that the amplification unit is displaced with the hinge (XP0) as a fulcrum, and the amplification unit and the movable unit are displaced. The amplification part urges the movable part at the connection position (XP3) of
The distance from the hinge to the connection position is longer than the distance from the hinge to the urging position.

Further, according to the invention of claim 1,
The oil flow path includes a first flow path (115) having a fixed flow path cross-sectional area and a second flow path (XV2, XV1) through which the oil flows by bypassing the first flow path.
The valve component is connected in the middle of the second flow path, and the communication and cutoff between the first oil hole and the second oil hole are switched by the movable part based on the rotation speed of the compressor, and the second By opening and closing the flow path, the flow rate of oil flowing through the oil flow path is adjusted.
Further, according to the invention of claim 2,
The valve component not only switches the communication and shutoff between the first oil hole and the second oil hole by the movable part, but also the first oil hole and the second oil hole by the movable part based on the rotation rate of the compressor. By adjusting the opening degree of at least one of the oil holes, the flow rate of oil flowing through the oil flow path is adjusted.
According to the inventions of claims 1 and 2 , a valve component is used as a valve mechanism for adjusting the flow rate of oil flowing through the oil flow path. The valve component can be easily miniaturized as compared with the conventional solenoid valve. Since the amplification part of the valve component functions as a lever, the amount of displacement corresponding to the temperature change of the drive part is amplified by the lever and transmitted to the movable part. The fact that the displacement amount of the drive unit is amplified by using a lever contributes to miniaturization as compared with the conventional solenoid valve that does not use such a lever. Therefore, it is possible to adjust the amount of oil return while suppressing the increase in the physique of the oil return device.

The reference numerals in parentheses attached to each component or the like indicate an example of the correspondence between the component or the like and the specific component or the like described in the embodiment described later.

It is a schematic diagram which shows the structure of the refrigerating cycle apparatus of 1st Embodiment. It is sectional drawing of the accumulator of 1st Embodiment. It is an enlarged view of the region II in FIG. It is a perspective view of the micro valve of 1st Embodiment. It is a side view of the micro valve of 1st Embodiment. FIG. 5 is a sectional view taken along line VI-VI of FIG. 5 is a sectional view taken along the line VII-VII of FIGS. 5 and 6. It is sectional drawing of the micro valve at the time of energization corresponding to FIG. FIG. 8 is a cross-sectional view taken along the line IX-IX of FIG. It is a figure which shows the relationship between the valve state of the microvalve and the flow rate of oil in 1st Embodiment. It is a figure which shows the relationship between the flow rate opening degree of a micro valve and the flow rate of oil in 2nd Embodiment. It is sectional drawing of the compressor of 3rd Embodiment. It is an enlarged view of the region XIII in FIG. It is sectional drawing of a part of the compressor of 4th Embodiment, and is the figure corresponding to FIG. It is sectional drawing of the micro valve of 5th Embodiment, and is the figure corresponding to FIG. It is an enlarged view of the region XVI in FIG.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In each of the following embodiments, the parts that are the same or equal to each other will be described with the same reference numerals.

(First Embodiment)
As shown in FIG. 1, the refrigeration cycle device 10 of the present embodiment includes an accumulator 12 to which the oil return device of the present invention is applied. The refrigeration cycle device 10 is mounted on a vehicle and is used in a vehicle air conditioner. The refrigerating cycle device 10 switches between cooling and heating inside the vehicle interior by switching the refrigerant flow. In addition to the accumulator 12, the refrigeration cycle device 10 includes a compressor 14, a radiator 16, a heating expansion valve 18, an outdoor heat exchanger 20, a cooling expansion valve 22, and an evaporator 24.

The compressor 14 is an electric compressor. The compressor 14 compresses and discharges the sucked refrigerant. The refrigerant contains oil for lubricating the sliding portion of the compressor 14. The oil is a refrigerating machine oil having incompatibility or poor solubility with the liquid phase refrigerant.

The radiator 16 dissipates the refrigerant discharged from the compressor 14. The radiator 16 is arranged inside the case 32 of the air conditioning unit 30. The radiator 16 is a heating heat exchanger that heats the air by exchanging heat between the air and the refrigerant toward the vehicle interior.

The heating expansion valve 18 decompresses and expands the refrigerant flowing out of the radiator 16 during heating. The outdoor heat exchanger 20 exchanges heat between the refrigerant and the air outside the vehicle interior. The cooling expansion valve 22 decompresses and expands the refrigerant flowing out of the outdoor heat exchanger 20 during cooling.

The evaporator 24 evaporates the refrigerant flowing out from the cooling expansion valve 22 during cooling. The evaporator 24 is arranged inside the case 32 on the upstream side of the air flow of the radiator 16. The evaporator 24 is a cooling heat exchanger that cools the air by exchanging heat between the air and the refrigerant toward the inside of the vehicle interior.

The accumulator 12 is connected to the refrigerant suction side of the compressor 14. That is, the accumulator 12 is installed between the refrigerant suction side of the compressor 14 and the refrigerant outlet side of the evaporator 24. The accumulator 12 separates the refrigerant sucked into the compressor 14 into a gas phase refrigerant and a liquid phase refrigerant, causes the separated vapor phase refrigerant to flow into the compressor 14, and stores the separated liquid phase refrigerant. The structure of the accumulator 12 will be described later.

The refrigeration cycle device 10 includes a first detour flow path 25 and a first solenoid valve 26 that opens and closes the first detour flow path 25. The first bypass flow path 25 is a flow path of the refrigerant that guides the refrigerant flowing out of the outdoor heat exchanger 20 to the accumulator 12 by bypassing the cooling expansion valve 22 and the evaporator 24. The first solenoid valve 26 is a first switching valve that switches between a refrigerant flow through which the refrigerant flows through the evaporator 24 and a refrigerant flow through which the refrigerant flows through the first detour flow path 25. A three-way valve may be used instead of the first solenoid valve 26.

The refrigeration cycle device 10 includes a second detour flow path 27 and a second solenoid valve 28 that opens and closes the second detour flow path 27. The second bypass flow path 27 is a flow path of the refrigerant that guides the refrigerant flowing out of the radiator 16 to the outdoor heat exchanger 20 by bypassing the heating expansion valve 18. The second solenoid valve 28 is a second switching valve that switches between a refrigerant flow through which the refrigerant flows through the heating expansion valve 18 and a refrigerant flow through which the refrigerant flows through the second detour flow path 27.

A blower 34 and an air mix door 36 are arranged inside the case 32. The blower 34 forms an air flow toward the vehicle interior. The air mix door 36 adjusts the mixing ratio of the air flowing through the radiator 16 and the air flowing around the radiator 16.

In the refrigeration cycle device 10 of the present embodiment, the first solenoid valve 26 is closed and the second solenoid valve 28 is opened during cooling. The position of the air mix door 36 is a position shown by a solid line. As a result, the refrigerant discharged from the compressor 14 has the radiator 16, the second detour flow path 27, the outdoor heat exchanger 20, the cooling expansion valve 22, the evaporator 24, and the accumulator 12, as shown by the solid arrows. And are sucked into the compressor 14. The air sent from the blower 34 passes through the evaporator 24 and does not pass through the radiator 16. Cooling is performed by the air cooled by the evaporator 24 heading toward the vehicle interior.

During heating, the first solenoid valve 26 opens and the second solenoid valve 28 closes. The position of the air mix door 36 is the position indicated by the broken line. As a result, the refrigerant discharged from the compressor 14 flows in the order of the radiator 16, the heating expansion valve 18, the outdoor heat exchanger 20, the first detour flow path 25, and the accumulator 12, as shown by the arrow of the broken line. It is sucked into the compressor 14. The air sent from the blower 34 passes through the evaporator 24 and the radiator 16 and heads toward the vehicle interior. Heating is performed by the air heated by the radiator 16 heading toward the vehicle interior.

Next, the configuration of the accumulator 12 will be described. As shown in FIG. 2, the accumulator 12 includes a tank 101, an inner pipe 102, an outer pipe 103, and a gas-liquid separation member 104.

Inside the tank 101, a space 101a is formed in which the refrigerant is separated into a gas phase refrigerant and a liquid phase refrigerant, and the separated liquid phase refrigerant and the oil contained in the refrigerant are stored. In the present embodiment, the space 101a inside the tank 101 corresponds to an oil storage chamber for storing oil.

The tank 101 has a tank main body portion 105 and a tank lid portion 106. Both the tank body 105 and the tank lid 106 are made of metal. The tank body 105 has a cylindrical shape with the upper end side open and the lower end side closed. The tank lid 106 is located on the upper end side of the tank body 105 and closes the upper end side of the tank body 105. The tank lid 106 is formed with a refrigerant inflow hole 107 and a refrigerant outflow hole 108.

The inner pipe 102 is arranged inside the tank 101. The inner pipe 102 is a cylinder extending in the vertical direction. The inner pipe 102 is made of metal. The inner pipe 102 may be made of synthetic resin. The upper end side of the inner pipe 102 is connected to the tank lid portion 106 so that the internal space of the inner pipe 102 communicates with the refrigerant outflow hole 108. The lower end 102a of the inner pipe 102 is open and is located above the bottom 105a of the tank main body 105.

The outer pipe 103 is arranged inside the tank 101. The outer pipe 103 is a cylinder extending in the vertical direction. The outer pipe 103 is made of metal. The outer pipe 103 may be made of synthetic resin. The outer pipe 103 is arranged outside the inner pipe 102 so that the inner pipe 102 and the outer pipe 103 form a double pipe. The upper end of the outer pipe 103 is open and is located below the tank lid 106. The outer pipe 103 has a bottom portion 103a. The bottom portion 103a of the outer pipe 103 is located between the bottom portion 105a of the tank main body portion 105 and the lower end 102a of the inner pipe 102 in the vertical direction.

The gas-liquid separation member 104 is arranged at a portion on the upper side of the inside of the tank 101. The gas-liquid separation member 104 has a cup shape with an open lower side. The upper portion of the gas-liquid separation member 104 extends in a direction intersecting the vertical direction. The upper portion of the gas-liquid separation member 104 faces the refrigerant inflow hole 107 in the vertical direction. The upper end of the outer pipe 103 is located below the upper portion of the gas-liquid separation member 104.

As shown in FIG. 3, a bottom communication hole 110 is formed in the bottom portion 103a of the outer pipe 103. The bottom communication hole 110 communicates the internal space of the outer pipe 103 with the space between the bottom 103a of the outer pipe 103 and the bottom 105a of the tank main body 105.

The accumulator 12 has a partition wall 111 provided between the bottom portion 103a of the outer pipe 103 and the bottom portion 105a of the tank main body 105. The partition wall 111 extends in the vertical direction. The upper end of the partition wall 111 is connected to the bottom portion 103a of the outer pipe 103. The lower end of the partition wall 111 is connected to the bottom portion 105a of the tank main body portion 105.

The partition wall 111 partitions the space between the bottom portion 103a of the outer pipe 103 and the bottom portion 105a of the tank main body 105 into an inner space 112 and an outer space 113. The inner space 112 is located inside the partition wall 111 and communicates with the bottom communication hole 110. The outer space 113 is located outside the partition wall 111 and communicates with the space inside the tank main body 105 and outside the outer pipe 103. A filter 114 for removing foreign matter is arranged in the outer space 113.

A partition wall hole 115 is formed in the partition wall 111. The partition wall hole 115 communicates the inner space 112 and the outer space 113. The space inside the tank body 105 and outside the outer pipe 103 communicates with the inner space of the outer pipe 103 via the outer space 113, the partition wall hole 115, the inner space 112, and the bottom communication hole 110.

The accumulator 12 has a valve module X0. The valve module X0 is provided on the outside of the bottom portion 105a of the tank main body portion 105.

[Valve module X0 configuration]
Here, the configuration of the valve module X0 will be described. The valve module X0 has a microvalve X1, a valve casing X2, a sealing member X3, two O-rings X4, X5, and two electrical wirings X6, X7.

The microvalve X1 is a plate-shaped valve component, and is mainly composed of a semiconductor chip. The microvalve X1 may or may not have parts other than the semiconductor chip. Therefore, the micro valve X1 can be configured in a small size. The length of the microvalve X1 in the thickness direction is, for example, 2 mm, the length in the longitudinal direction orthogonal to the thickness direction is, for example, 10 mm, and the length in the lateral direction orthogonal to both the longitudinal direction and the thickness direction. Is, for example, 5 mm, but is not limited thereto.

The micro valve X1 functions as an on-off valve. Opening and closing is switched by switching between energization and non-energization of the micro valve X1. Specifically, the micro valve X1 is a normally closed valve that opens when energized and closes when not energized.

The electrical wirings X6 and X7 extend from the surface of the two plates on the front and back of the microvalve X1 opposite to the valve casing X2, pass through the sealing member X3 and the valve casing X2, and pass through the valve module. It is connected to a power supply outside X0. As a result, power is supplied from the power source to the micro valve X1 through the electric wires X6 and X7.

The valve casing X2 is a resin casing that houses the microvalve X1. The valve casing X2 is formed by resin molding containing polyphenylene sulfide as a main component. The valve casing X2 is a box body having a bottom wall on one side and an open side on the other side. The bottom wall of the valve casing X2 is interposed between the bottom portion 105a and the microvalve X1 so that the microvalve X1 and the bottom portion 105a do not come into direct contact with each other. Then, one surface of the bottom wall is in contact with and fixed to the bottom portion 105a, and the other surface is in contact with and fixed to one of the two plate surfaces of the microvalve X1. In this way, the valve casing X2 can absorb the difference in the linear expansion coefficient between the micro valve X1 and the tank body 105. This is because the coefficient of linear expansion of the valve casing X2 is a value between the coefficient of linear expansion of the microvalve X1 and the coefficient of linear expansion of the tank body 105.

Further, the bottom wall of the valve casing X2 has a plate-shaped base portion X20 facing the microvalve X1 and a pillar-shaped first protruding portion X21 and a second protruding portion X21 protruding from the base portion X20 in a direction away from the microvalve X1. It has a portion X22.

The first protruding portion X21 is fitted into the first opening 116 formed in the bottom portion 105a. The first opening 116 communicates with the inner space 112. The first protrusion X21 is formed with a first communication hole XV1 that penetrates from the microvalve X1 side end to the inner space 112 side end. The first communication hole XV1 communicates with the inner space 112.

The second protruding portion X22 is fitted in the second opening 117 formed in the bottom portion 105a. The second opening 117 communicates with the outer space 113. The second protrusion X22 is formed with a second communication hole XV2 that penetrates from the microvalve X1 side end to the outer space 113 side end. The second communication hole XV2 communicates with the outer space 113.

The sealing member X3 is a member made of epoxy resin that seals the other open side of the valve casing X2. The sealing member X3 covers the plate surface of the two plate surfaces on the front and back sides of the micro valve X1 on the side opposite to the bottom wall side of the valve casing X2. Further, the sealing member X3 covers the electric wirings X6 and X7 to realize waterproofing and insulation of the electric wirings X6 and X7. The sealing member X3 is formed by resin potting or the like.

The O-ring X4 is attached to the outer periphery of the first protruding portion X21 and seals between the bottom portion 105a and the first protruding portion X21 to suppress oil leakage to the outside of the tank 101. The O-ring X5 is attached to the outer periphery of the second protruding portion X22 and seals between the bottom portion 105a and the second protruding portion X22 to suppress oil leakage to the outside of the tank 101.

Here, the configuration of the micro valve X1 will be further described. As shown in FIGS. 4 and 5, the microvalve X1 is a MEMS having a first outer layer X11, an intermediate layer X12, and a second outer layer X13, all of which are semiconductors. MEMS is an abbreviation for Micro Electro Mechanical Systems. The first outer layer X11, the intermediate layer X12, and the second outer layer X13 are rectangular plate-shaped members having the same outer shape, and the first outer layer X11, the intermediate layer X12, and the second outer layer X13 are laminated in this order. That is, the intermediate layer X12 is sandwiched between the first outer layer X11 and the second outer layer X13 from both sides. Of the first outer layer X11, the intermediate layer X12, and the second outer layer X13, the second outer layer X13 is arranged on the side closest to the bottom wall of the valve casing X2. The structures of the first outer layer X11, the intermediate layer X12, and the second outer layer X13, which will be described later, are formed by a semiconductor manufacturing process such as chemical etching.

The first outer layer X11 is a conductive semiconductor member having a non-conductive oxide film on its surface. As shown in FIG. 4, two through holes X14 and X15 penetrating the front and back are formed in the first outer layer X11. The microvalve X1 side ends of the electrical wirings X6 and X7 are inserted into the through holes X14 and X15, respectively.

The second outer layer X13 is a conductive semiconductor member having a non-conductive oxide film on its surface. As shown in FIGS. 4, 6, and 7, the second outer layer X13 is formed with a first oil hole X16 and a second oil hole X17 penetrating the front and back surfaces. As shown in FIG. 7, the first oil hole X16 communicates with the first communication hole XV1 of the valve casing X2, and the second oil hole X17 communicates with the second communication hole XV2 of the valve casing X2. The hydraulic diameters of the first oil hole X16 and the second oil hole X17 are, for example, 0.1 mm or more and 3 mm or less, but are not limited thereto.

The intermediate layer X12 is a conductive semiconductor member. Since the intermediate layer X12 comes into contact with the oxide film of the first outer layer X11 and the oxide film of the second outer layer X13, both the first outer layer X11 and the second outer layer X13 are electrically non-conducting. As shown in FIG. 6, the intermediate layer X12 has a first fixed portion X121, a second fixed portion X122, a plurality of first ribs X123, a plurality of second ribs X124, a spine X125, an arm X126, a beam X127, and a movable layer. It has a part X128.

The first fixing portion X121 is a member fixed to the first outer layer X11 and the second outer layer X13. The first fixed portion X121 is formed so as to surround the second fixed portion X122, the first rib X123, the second rib X124, the spine X125, the arm X126, the beam X127, and the movable portion X128 in the same oil chamber X19. There is. The oil chamber X19 is a chamber surrounded by a first fixing portion X121, a first outer layer X11, and a second outer layer X13. The first fixed portion X121, the first outer layer X11, and the second outer layer X13 correspond to the base as a whole. The electrical wirings X6 and X7 are electrical wirings for changing and displacing the temperatures of the plurality of first ribs X123 and the plurality of second ribs X124.

The fixing of the first fixing portion X121 to the first outer layer X11 and the second outer layer X13 prevents oil from leaking from the oil chamber X19 through the oil chamber X19 other than the first oil hole X16 and the second oil hole X17. It is done in such a form.

The second fixing portion X122 is fixed to the first outer layer X11 and the second outer layer X13. The second fixed portion X122 is surrounded by the first fixed portion X121 and is arranged away from the first fixed portion X121.

The plurality of first ribs X123, the plurality of second ribs X124, the spine X125, the arm X126, the beam X127, and the movable portion X128 are not fixed to the first outer layer X11 and the second outer layer X13, and are the first. It is displaceable with respect to the outer layer X11 and the second outer layer X13.

The spine X125 has an elongated rod shape extending in the lateral direction in the rectangular shape of the intermediate layer X12. One end of the spine X125 in the longitudinal direction is connected to the beam X127.

The plurality of first ribs X123 are arranged on one side of the spine X125 in a direction orthogonal to the longitudinal direction of the spine X125. The plurality of first ribs X123 are arranged in the longitudinal direction of the spine X125. Each first rib X123 has an elongated rod shape and can be expanded and contracted according to the temperature.

Each first rib X123 is connected to the first fixing portion X121 at one end in the longitudinal direction thereof and to the spine X125 at the other end. Each of the first ribs X123 is skewed with respect to the spine X125 so as to approach the spine X125 side from the first fixing portion X121 side so as to be offset toward the beam X127 side in the longitudinal direction of the spine X125. .. The plurality of first ribs X123 extend in parallel with each other.

The plurality of second ribs X124 are arranged on the other side of the spine X125 in a direction orthogonal to the longitudinal direction of the spine X125. The plurality of second ribs X124 are arranged in the longitudinal direction of the spine X125. Each second rib X124 has an elongated rod shape and can be expanded and contracted according to the temperature.

Each second rib X124 is connected to the second fixing portion X122 at one end in the longitudinal direction thereof and to the spine X125 at the other end. Each of the second ribs X124 is skewed with respect to the spine X125 so as to approach the spine X125 side from the second fixed portion X122 side so as to be offset toward the beam X127 side in the longitudinal direction of the spine X125. .. The plurality of second ribs X124 extend in parallel with each other.

The plurality of first ribs X123, the plurality of second ribs X124, and the spine X125 correspond to the drive unit as a whole.

The arm X126 has an elongated rod shape extending non-orthogonally and parallel to the spine X125. One end of the arm X126 in the longitudinal direction is connected to the beam X127, and the other end is connected to the first fixing portion X121.

The beam X127 has an elongated rod shape extending in a direction intersecting the spine X125 and the arm X126 at about 90 °. One end of the beam X127 is connected to the movable portion X128. The arm X126 and the beam X127 correspond to the amplification portion as a whole.

The connection position XP1 of the arm X126 and the beam X127, the connection position XP2 of the spine X125 and the beam X127, and the connection position XP3 of the beam X127 and the movable portion X128 are arranged in this order along the longitudinal direction of the beam X127. Then, assuming that the connection point between the first fixing portion X121 and the arm X126 is the hinge XP0, the connection position from the hinge XP0 is more than the linear distance from the hinge XP0 to the connection position XP2 in the plane parallel to the plate surface of the intermediate layer X12. The straight line distance to XP3 is longer.

The movable portion X128 has a rectangular shape whose outer shape extends in a direction of approximately 90 ° with respect to the longitudinal direction of the beam X127. The movable portion X128 can move integrally with the beam X127 in the oil chamber X19. Then, by moving in this way, the movable portion X128 communicates the first oil hole X16 and the second oil hole X17 with each other via the oil chamber X19 when it is in a certain position, and when it is in another position, it is the first. The oil hole X16 and the second oil hole X17 are shut off in the oil chamber X19. The movable portion X128 has a frame shape surrounding the through hole X120 penetrating the front and back of the intermediate layer X12. Therefore, the through hole X120 also moves integrally with the movable portion X128. The through hole X120 is a part of the oil chamber X19.

Further, at the first application point X129 in the vicinity of the portion of the first fixed portion X121 connected to the plurality of first ribs X123, the electric wiring X6 passing through the through hole X14 of the first outer layer X11 shown in FIG. The microvalve X1 side end of is connected. Further, the microvalve X1 side end of the electric wiring X7 passing through the through hole X15 of the first outer layer X11 shown in FIG. 4 is connected to the second application point X130 of the second fixing portion X122.

[Operation of valve module X0]
Here, the operation of the valve module X0 will be described. When the microvalve X1 is energized, a voltage is applied from the electrical wirings X6 and X7 to the first application point X129 and the second application point X130. Then, a current flows through the plurality of first ribs X123 and the plurality of second ribs X124. Due to this current, the plurality of first ribs X123 and the plurality of second ribs X124 generate heat and their temperatures rise. As a result, each of the plurality of first ribs X123 and the plurality of second ribs X124 expands in the longitudinal direction thereof.

As a result of such thermal expansion due to the temperature rise, the plurality of first ribs X123 and the plurality of second ribs X124 urge the spine X125 toward the connection position XP2. The urged spine X125 pushes the beam X127 at the connection position XP2. In this way, the connection position XP2 corresponds to the urging position. As a result, the member including the beam X127 and the arm X126 changes their postures integrally with the hinge XP0 as the fulcrum and the connection position XP2 as the power point. As a result, the movable portion X128 connected to the end of the beam X127 opposite to the arm X126 also moves in the longitudinal direction to the side where the spine X125 pushes the beam X127. As a result of the movement, the movable portion X128 reaches a position where the tip in the moving direction abuts on the first fixed portion X121, as shown in FIGS. 8 and 9. Hereinafter, this position of the movable portion X128 is referred to as an energized position.

As described above, the beam X127 and the arm X126 function as a lever having the hinge XP0 as a fulcrum, the connection position XP2 as a force point, and the connection position XP3 as an action point. As described above, the linear distance from the hinge XP0 to the connection position XP3 is longer than the linear distance from the hinge XP0 to the connection position XP2 in the plane parallel to the plate surface of the intermediate layer X12. Therefore, the amount of movement of the connection position XP3, which is the point of action, is larger than the amount of movement of the connection position XP2, which is the point of effort. Therefore, the amount of displacement due to thermal expansion is amplified by the lever and transmitted to the movable portion X128.

As shown in FIGS. 8 and 9, when the movable portion X128 is in the energized position, the through hole X120 overlaps with the first oil hole X16 and the second oil hole X17 in the direction orthogonal to the plate surface of the intermediate layer X12. In that case, the first oil hole X16 and the second oil hole X17 communicate with each other through the through hole X120 which is a part of the oil chamber X19. As a result, oil can flow between the first communication hole XV1 and the second communication hole XV2 through the first oil hole X16, the through hole X120, and the second oil hole X17. That is, the micro valve X1 opens.

At this time, the oil flow path in the micro valve X1 has a U-turn structure. Specifically, the oil flows into the microvalve X1 from one surface of the microvalve X1, passes through the microvalve X1, and flows out of the microvalve X1 from the same surface of the microvalve X1. Similarly, the oil flow path in the valve module X0 also has a U-turn structure. Specifically, the oil flows into the valve module X0 from one surface of the valve module X0, passes through the inside of the valve module X0, and flows out of the valve module X0 from the same side surface of the valve module X0. The direction orthogonal to the plate surface of the intermediate layer X12 is the stacking direction of the first outer layer X11, the intermediate layer X12, and the second outer layer X13.

Further, when the micro valve X1 is not energized, the voltage application from the electric wirings X6 and X7 to the first application point X129 and the second application point X130 is stopped. Then, the current stops flowing through the plurality of first ribs X123 and the plurality of second ribs X124, and the temperatures of the plurality of first ribs X123 and the plurality of second ribs X124 decrease. As a result, each of the plurality of first ribs X123 and the plurality of second ribs X124 contracts in the longitudinal direction thereof.

As a result of such thermal contraction due to the temperature decrease, the plurality of first ribs X123 and the plurality of second ribs X124 urge the spine X125 to the side opposite to the connection position XP2. The urged spine X125 pulls the beam X127 at the connection position XP2. As a result, the member including the beam X127 and the arm X126 changes their postures integrally with the hinge XP0 as the fulcrum and the connection position XP2 as the power point. As a result, the movable portion X128 connected to the end of the beam X127 opposite to the arm X126 also moves in the longitudinal direction to the side where the spine X125 pulls the beam X127. As a result of the movement, the movable portion X128 reaches a position where it does not abut on the first fixed portion X121 as shown in FIGS. 6 and 7. Hereinafter, this position of the movable portion X128 is referred to as a non-energized position.

As shown in FIGS. 6 and 7, when the movable portion X128 is in the non-energized position, the through hole X120 overlaps with the first oil hole X16 in the direction orthogonal to the plate surface of the intermediate layer X12, but in that direction. It does not overlap with the second oil hole X17. The second oil hole X17 overlaps with the movable portion X128 in the direction orthogonal to the plate surface of the intermediate layer X12. That is, the second oil hole X17 is closed by the movable portion X128. In this case, the first oil hole X16 and the second oil hole X17 are blocked in the oil chamber X19. As a result, the flow of oil between the first communication hole XV1 and the second communication hole XV2 through the first oil hole X16 and the second oil hole X17 is hindered. That is, the micro valve X1 is closed.

Next, the operation of the accumulator 12 will be described.

As shown by the arrow R0 in FIG. 2, the refrigerant flows into the tank 101 through the refrigerant inflow hole 107, then collides with the gas-liquid separation member 104 and is separated into the liquid-phase refrigerant and the gas-phase refrigerant. The separated liquid-phase refrigerant and the oil contained in the refrigerant go straight down as shown by the arrow R1 and are stored inside the tank 101. After that, the separation of the liquid phase refrigerant and the oil proceeds. As shown in FIG. 2, the oil R1b collects below the liquid phase refrigerant R1a. That is, the oil collects in a portion on the bottom side of the tank 101.

On the other hand, the separated vapor phase refrigerant flows inside the tank 101 as shown by the arrow R2 in FIG. That is, the gas phase refrigerant flows into the inside of the outer pipe 103 from the upper end of the outer pipe 103. The vapor phase refrigerant descends between the inner peripheral surface of the outer pipe 103 and the outer peripheral surface of the inner pipe 102. The lowered gas phase refrigerant flows into the inside of the inner pipe 102 from the lower end 102a of the inner pipe 102, and rises inside the inner pipe 102. The increased vapor phase refrigerant flows out from the refrigerant outflow hole 108 and is sucked into the compressor 14.

The oil collected on the bottom side of the tank 101 passes through the outer space 113, the partition wall hole 115, and the inner space 112 and is sucked into the outer pipe 103 from the bottom communication hole 110 as shown by the arrow O1 in FIG. Will be done. This oil flow is formed by the flow of the gas phase refrigerant shown by the arrow R2 in FIG. Therefore, the bottom communication hole 110 corresponds to an oil suction portion where oil is sucked by the flow of the gas phase refrigerant. At this time, the filter 114 prevents foreign matter from entering the outer pipe 103. The oil flows out from the refrigerant outflow hole 108 together with the gas phase refrigerant and is returned to the compressor 14.

When the microvalve X1 is open, the oil flow of arrow O2 in FIG. 3 is formed in addition to the oil flow of arrow O1 in FIG. That is, the oil flows in the outer space 113, the second communication hole XV2, the micro valve X1, the first communication hole XV1, and the inner space 112 in this order. The oil that has passed through the microvalve X1 joins the oil that has passed through the partition wall hole 115 in the inner space 112. On the other hand, when the micro valve X1 is closed, the oil flow of arrow O2 in FIG. 3 is not formed.

In the present embodiment, when the micro valve X1 is open, oil flows as shown by arrows O1 and O2. Therefore, the outer space 113, the partition wall hole 115, the inner space 112, the bottom communication hole 110, the second communication hole XV2 and the first communication hole XV1 as a whole are oiled from the oil storage chamber toward the sliding portion of the compressor. Corresponds to the oil flow path through which. Further, the bottom portion 103a of the outer pipe 103, the bottom portion 105a of the tank main body portion 105, and the partition wall 111 form an inner space 112 and an outer space 113. The bottom portion 103a of the outer pipe 103 forms a bottom communication hole 110. The partition wall 111 forms a partition wall hole 115. The valve casing X2 forms the first communication hole XV1 and the second communication hole XV2. Therefore, the bottom portion 103a of the outer pipe 103, the bottom portion 105a of the tank main body portion 105, the partition wall 111, and the valve casing X2 correspond to the flow path forming portion forming the oil flow path as a whole.

Further, the micro valve X1 is provided in the valve casing X2. Therefore, the valve component is provided in the flow path forming portion that forms the oil flow path. The first oil hole X16 of the micro valve X1 communicates with the first communication hole XV1 of the valve casing X2. Therefore, the first oil hole X16 communicates with a part of the oil flow path. The second oil hole X17 of the micro valve X1 communicates with the second communication hole XV2 of the valve casing X2. Therefore, the second oil hole X17 communicates with another part of the oil flow path.

Next, the effect of this embodiment will be described. According to this embodiment, the micro valve X1 is used as the valve mechanism. The micro valve X1 can be easily miniaturized as compared with a conventional solenoid valve. One of the reasons is that the microvalve X1 is formed of a semiconductor chip as described above. Further, as described above, the fact that the displacement amount due to thermal expansion is amplified by using a lever also contributes to the miniaturization as compared with the solenoid valve that does not use such a lever.

Further, unlike the present embodiment, when the accumulator 12 is not provided with the micro valve X1, the oil passes through the partition wall hole 115 which is the oil return hole and is sucked into the inside of the outer pipe 103. At this time, the size of the partition wall hole 115 is fixed. At this time, the flow rate of the oil passing through the partition wall hole 115 is determined by the flow rate of the gas phase refrigerant flowing through the outer pipe 103 and the inner pipe 102. Therefore, when the flow rate of the refrigerant flowing through the entire cycle is small and the flow rate of the gas phase refrigerant is slow, the flow rate of the oil passing through the partition wall hole 115 is small. The amount of oil returned, which is the flow rate of oil returned to the sliding portion of the compressor 14, is small. If the oil return amount continues to be small, the compressor 14 will fail.

On the other hand, in the present embodiment, the accumulator 12 includes a microvalve X1. As described above, when the micro valve X1 is closed, the oil passes through the partition wall hole 115 and does not pass through the micro valve X1. When the microvalve X1 is open, oil passes through both the partition wall hole 115 and the microvalve X1. Therefore, as shown in FIG. 10, when the micro valve X1 is closed, the flow rate of the oil flowing into the inside of the outer pipe 103 is the first flow rate A1 which is larger than 0. When the micro valve X1 is open, the flow rate of the oil flowing into the outer pipe 103 is the second flow rate A2, which is larger than the first flow rate A1. By switching the opening and closing of the micro valve X1 in this way, the flow rate of the oil can be adjusted in two stages of the first flow rate A1 and the second flow rate A2.

Therefore, when the flow rate of the refrigerant during the cycle is larger than the predetermined amount, the micro valve X1 is closed. The case where the flow rate of the refrigerant during the cycle is larger than the predetermined amount is, for example, the case where the rotation speed of the compressor 14 is larger than the predetermined rotation speed. When the flow rate of the refrigerant during the cycle is less than a predetermined amount, the microvalve X1 is opened. The case where the flow rate of the refrigerant during the cycle is smaller than the predetermined amount is, for example, the case where the rotation speed of the compressor 14 is smaller than the predetermined rotation speed. By opening the micro valve X1, the amount of oil return can be increased as compared with the time when the valve is closed. This makes it possible to avoid a failure of the compressor 14.

As described above, according to the present embodiment, it is possible to adjust the amount of oil reconstituted while suppressing the increase in the physique of the accumulator 12.

(Second Embodiment)
In the present embodiment, the flow path opening degree of the micro valve X1 can be changed to an arbitrary size. Other than that, the configuration of the accumulator 12 and the refrigerating cycle device 10 including the accumulator 12 is the same as that of the first embodiment.

Specifically, in the present embodiment, the voltage applied to the first application point X129 and the second application point X130 in FIG. 8 is PWM controlled. The PWM control is a control that repeatedly switches between energization and non-energization. At this time, the larger the duty ratio, the larger the power supplied. Duty ratio is the ratio of energization time to a certain period. The larger the electric power, the higher the temperature and the larger the amount of thermal expansion. Therefore, the larger the duty ratio, the larger the amount of movement during energization with respect to the non-energization. Therefore, the position of the movable portion X128 can be continuously changed from the fully closed position to the fully open position by PWM control.

Therefore, the micro valve X1 continuously changes the duty ratio from 0% to 100%, so that the opening degree of the flow path is changed from 0% to 100% as shown in FIG. It can be changed linearly. The flow path cross-sectional area when the opening degree of the flow path is larger than 0% is a magnitude for reducing the pressure of the refrigerant. By changing the flow path opening of the micro valve X1 to an arbitrary size, the flow rate of the oil flowing into the outer pipe 103 is adjusted to an arbitrary size between the first flow rate A1 and the second flow rate A2. be able to.

Here, unlike the present embodiment, when the accumulator 12 does not include the microvalve X1, the oil passes through the partition wall hole 115 and is sucked into the inside of the outer pipe 103. At this time, the size of the partition wall hole 115 is fixed. Therefore, the oil return amount cannot be adjusted to a desired amount. Therefore, when the rotation speed of the compressor 14 fluctuates, it is not possible to maintain the optimum oil rate for increasing the efficiency of the compressor 14. The oil rate is the ratio of oil to the total refrigerant.

On the other hand, according to the present embodiment, as described above, by changing the opening degree of the micro valve X1, the oil return amount is set to an arbitrary size between the first flow rate A1 and the second flow rate A2. Can be adjusted. Therefore, the opening degree of the micro valve X1 is controlled based on the rotation speed of the compressor so that the optimum oil return amount is obtained according to the rotation speed of the compressor. This optimum oil return amount is an oil return amount set so as to obtain an optimum oil rate according to the rotation speed of the compressor. As a result, even if the rotation speed of the compressor fluctuates, the oil can be returned in the optimum amount, and the optimum oil rate can be maintained.

In this embodiment, the partition wall hole 115 is formed in the partition wall 111. However, the partition wall hole 115 may not be formed in the partition wall 111. In this case, by changing the opening degree of the micro valve X1, the oil return amount can be adjusted to an arbitrary size between zero and the maximum value.

(Third Embodiment)
As shown in FIG. 12, in the present embodiment, the oil return device of the present invention is applied to the oil separator 15. The oil separator 15 separates the oil contained in the refrigerant discharged from the compressor 14, and returns the separated oil to the sliding portion of the compressor 14. In the present embodiment, the oil separator 15 is configured to be integrated with the compressor 14.

The compressor 14 includes a housing 201, an electric motor unit 202, and a compression mechanism unit 203. Housing 201 is a closed container. The housing 201 accommodates the motor unit 202 and the compression mechanism unit 203. A discharge chamber 204 and an oil storage chamber 205 are formed inside the housing 201. The electric motor unit 202 rotates the rotation shaft 206 of the compression mechanism unit 203. The compression mechanism unit 203 compresses the refrigerant by the rotation of the rotating shaft 206, and discharges the compressed refrigerant to the discharge chamber 204. The compression mechanism unit 203 of the present embodiment is a scroll type, but may be another type such as a swash plate type.

The housing 201 has a cylindrical first housing 211, a bottomed cylindrical second housing 212 joined to one end side of the first housing 211, and a bottomed cylinder joined to the other end side of the first housing 211. It includes a third housing 213 in the shape of a cylinder and a fourth housing 214 joined to the inner peripheral surface of the end portion of the third housing 213. The space surrounded by the first housing 211, the second housing 212, and the third housing 213 is a storage chamber for accommodating the motor unit 202 and the compression mechanism unit 203. The space surrounded by the third housing 213 and the fourth housing 214 is the oil storage chamber 205.

The compression mechanism unit 203 includes a movable scroll 221, a fixed scroll 222, and a rotation axis 206. The movable scroll 221 is not fixed to the housing 201. The movable scroll 221 is connected to the rotating shaft 206 via a crank mechanism. The fixed scroll 222 is fixed to the housing 201. The fixed scroll 222 is arranged so as to face the movable scroll 221 in the axial direction of the rotating shaft 206. The rotating shaft 206 is supported by a main bearing 224 and an auxiliary bearing 225 fixed to the housing 201.

When the rotation shaft 206 rotates, the movable scroll 221 revolves by the crank mechanism. The movable scroll 221 and the fixed scroll 222 each have a spiral groove. A plurality of working chambers 226 formed by the meshing of these grooves reduce the volume. As a result, the refrigerant supplied to the working chamber 226 is compressed.

A discharge chamber 204 is formed on the opposite side of the movable scroll 221 side with respect to the fixed scroll 222. The discharge chamber 204 communicates with the working chamber 226 via the discharge port 227. The refrigerant compressed in the operating chamber 226 is discharged to the discharge chamber 204.

Further, the fixed scroll 222 is formed with an oil return passage 228. The oil return passage 228 communicates with the sliding interface between the movable scroll 221 and the fixed scroll 222. An oil supply passage 229 is formed in the movable scroll 221. An oil supply passage 230 is formed inside the rotating shaft 206. The oil supply passages 229 and 230 communicate with the oil return passage 228.

The compressor 14 further includes a first cylinder 231 and a second cylinder 232, a refrigerant discharge pipe 233, an oil transport pipe 234, and a flow rate adjusting unit 235. In the present embodiment, the first cylinder 231 and the second cylinder 232, the refrigerant discharge pipe 233, the oil transport pipe 234, the flow rate adjusting unit 235, the third housing 213, and the fourth housing 214 are provided. It constitutes an oil separator 15.

The first tubular body 231 has a cylindrical shape with an open upper end and a bottom at the lower end. The second tubular body 232 has a cylindrical shape in which the upper end and the lower end are open. The second tubular body 232 has a large diameter portion having a large outer diameter and a small diameter portion having a smaller outer diameter than the large diameter portion. The small diameter portion is located below the large diameter portion. The second cylinder 232 is arranged concentrically with respect to the first cylinder 231 inside the first cylinder 231. The large diameter portion of the second cylinder 232 is fixed to the upper end of the first cylinder 231. A refrigerant inflow port 231b is formed at a position of the peripheral wall portion 231a of the first cylinder 231 facing the small diameter portion of the second cylinder 232. The refrigerant inlet side of the radiator 16 shown in FIG. 1 is connected to the upper end of the second cylinder 232.

One end side of the refrigerant discharge pipe 233 is connected to the discharge chamber 204. The other end of the refrigerant discharge pipe 233 is connected to the refrigerant inflow port 231b. Refrigerant flows from the discharge chamber 204 to the refrigerant inlet 231b via the refrigerant discharge pipe 233.

The lower end portion of the first cylinder 231 penetrates the upper part of the third housing 213 and is located in the oil storage chamber 205. An oil outlet 231c is formed in a portion of the peripheral wall portion 231a of the first cylinder 231 located in the oil storage chamber 205.

The oil storage chamber 205 stores the oil that has flowed out from the oil outlet 231c. That is, the oil storage chamber 205 stores the oil separated from the refrigerant. A magnet 236 is arranged in the oil storage chamber 205. The magnet 236 is arranged at a position where oil drops from the oil outlet 231c to the magnet 236. The magnet 236 is attached to a mounting bracket 237 fixed to the third housing 213.

The oil transport pipe 234 forms an internal flow path through which oil flows from the oil storage chamber 205 toward the sliding portion of the compressor 14. One end side of the oil transport pipe 234 is connected to an oil transport port 213a provided at the bottom of the third housing 213. The other end of the oil transport pipe 234 is connected to the oil return port 211a provided in the first housing 211. The oil return port 211a communicates with the oil return passage 228. The oil storage chamber 205 and the oil return passage 228 communicate with each other via the oil transport pipe 234.

The flow rate adjusting unit 235 is provided in the middle of the oil transport pipe 234. The flow rate adjusting unit 235 adjusts the flow rate of the oil flowing through the flow path inside the oil transport pipe 234.

As shown in FIG. 13, the flow rate adjusting unit 235 has a valve module X0 and a block body 240. The valve module X0 is connected to the block body 240. The configuration of the valve module X0 is the same as that of the first embodiment. The oil transport pipe 234 includes a first pipe 234a and a second pipe 234b. The flow path 234c inside the first pipe 234a communicates with the oil storage chamber 205. The flow path 234d inside the second pipe 234b communicates with the oil return passage 228.

The block body 240 is a connecting member that connects the valve module X0, the first pipe 234a, and the second pipe 234b. Inside the block body 240, a first flow path 241, a second flow path 242, and a third flow path 243 are formed. Inside the block body 240, the first flow path 241 and the second flow path 242 communicate with each other via the third flow path 243. The third flow path 243 is a flow path having a smaller flow path cross-sectional area than each of the first flow path 241 and the second flow path 242. The first pipe 234a is connected to the first flow path 241. The second pipe 234b is connected to the second flow path 242.

The block body 240 is formed with a first opening 241a communicating with the first flow path 241 and a second opening 242a communicating with the second flow path 242. The second opening 242a is arranged next to the first opening 241a. The first protruding portion X21 and the second protruding portion X22 of the valve module X0 are inserted into the first opening 241a and the second opening 242a, respectively. As a result, the flow path 234c inside the first pipe 234a communicates with the first communication hole XV1. The flow path 234d inside the second pipe 234b communicates with the second communication hole XV2.

Next, the operation of the compressor 14 and the oil separator 15 will be described.

The refrigerant compressed in the operating chamber 226 flows into the discharge chamber 204 through the discharge port 227. The refrigerant that has flowed into the discharge chamber 204 flows through the refrigerant discharge pipe 233 and flows into the inside of the first cylinder 231 from the refrigerant inlet 231b. The inflowing refrigerant forms a swirling flow in the space between the inner peripheral surface of the first cylinder 231 and the outer peripheral surface of the second cylinder 232. Oil and foreign matter mixed in the refrigerant are separated by the centrifugal force of the swirling flow. Therefore, the first cylinder 231 and the second cylinder 232 and the refrigerant inlet 231b correspond to the separation portion that separates the oil portion from the refrigerant as a whole. The refrigerant from which the oil has been separated flows out from the second cylinder 232 and flows toward the radiator 16.

The separated oil and foreign matter flow down along the inner wall of the first cylinder 231. Oil and foreign matter fall from the oil outlet 231c and flow into the oil storage chamber 205. At this time, the oil and the foreign matter fall on the upper surface of the magnet 236. As a result, the metallic foreign matter contained in the oil is attracted to the magnet 236. The oil from which the metal foreign matter has been removed is stored in the oil storage chamber 205.

The oil stored in the oil storage chamber 205 flows into the oil return passage 228 via the oil transport pipe 234 and the flow rate adjusting unit 235. Specifically, as shown in FIG. 13, the oil flow indicated by the arrow O3 in FIG. 13 is formed inside the flow rate adjusting unit 235. That is, the oil stored in the oil storage chamber 205 is the flow path inside the flow path 234c inside the first pipe 234a, the first flow path 241 and the third flow path 243, the second flow path 242, and the flow path inside the second pipe 234b. It flows in the order of 234d.

When the microvalve X1 is open, the oil flow of arrow O4 in FIG. 13 is formed in addition to the oil flow of arrow O3 in FIG. That is, the oil flows in the first flow path 241, the first communication hole XV1, the micro valve X1, the second communication hole XV2, and the second communication flow path 242 in this order. In other words, the oil flows around the third flow path 243. The oil that has passed through the micro valve X1 joins the oil that has passed through the third flow path 243. On the other hand, when the micro valve X1 is closed, the oil flow of arrow O4 in FIG. 13 is not formed. The flow of oil from the oil storage chamber 205 to the oil return passage 228 is formed by the pressure difference between the oil storage chamber 205 and the accommodation chamber of the housing 201.

The oil flowing through the oil return passage 228 is supplied to the sliding interface between the movable scroll 221 and the fixed scroll 222. Further, the oil flowing out from the oil return passage 228 flows through the oil supply passages 229 and 230. As a result, oil is supplied to the main bearing 224, the auxiliary bearing 225, and the like.

In this way, the oil contained in the refrigerant discharged from the compressor 14 is separated by the oil separator 15. The separated oil is returned to the sliding interface between the movable scroll 221 and the fixed scroll 222, and the sliding portion of the compression mechanism portion 203 such as the main bearing 224 and the auxiliary bearing 225.

In the present embodiment, when the micro valve X1 is open, oil flows as shown by arrows O3 and O4. Therefore, the internal flow path 234c of the first pipe 234a, the first flow path 241 and the third flow path 243, the second flow path 242, the internal flow path 234d of the second pipe 234b, the first communication hole XV1 and the first passage hole XV1. The two communication holes XV2 correspond to the oil flow path through which the oil flows from the oil storage chamber toward the sliding portion of the compressor as a whole. Further, the first pipe 234a forms a flow path 234c. The second pipe 234b forms a flow path 234d. The block body 240 forms the first flow path 241 and the third flow path 243, and the second flow path 242. The valve casing X2 forms the first communication hole XV1 and the second communication hole XV2. Therefore, the first pipe 234a, the second pipe 234b, the block body 240, and the valve casing X2 correspond to the flow path forming portion forming the oil flow path as a whole. Further, the micro valve X1 is provided in the valve casing X2. Therefore, the valve component is provided in the flow path forming portion that forms the oil flow path.

Next, the features of this embodiment will be described. In the present embodiment, the micro valve X1 is used as the valve mechanism for adjusting the flow rate of the oil, as in the first embodiment. As described in the first embodiment, the microvalve X1 can be downsized as compared with the conventional solenoid valve.

Further, unlike the present embodiment, when the oil separator 15 does not include the micro valve X1, the oil passes through the third flow path 243 and is sucked into the inside of the outer pipe 103. The size of the third flow path 243 is fixed. Therefore, the flow rate of the oil passing through the third flow path 243 is constant. When the number of revolutions of the compressor 14 is high and the flow rate of the refrigerant discharged from the compressor 14 is high, the oil may not be returned from the oil storage chamber 205 to the inside of the compressor 14 in time, and the oil may overflow from the oil storage chamber 205. .. The overflowing oil flows into the radiator 16 and the like together with the refrigerant. Therefore, the oil inside the compressor 14 is insufficient.

On the other hand, in the present embodiment, the oil separator 15 includes a flow rate adjusting unit 235 including a micro valve X1. As described above, when the micro valve X1 is closed, the oil passes through the third flow path 243 and does not pass through the micro valve X1. When the microvalve X1 is open, the oil passes through both the third flow path 243 and the microvalve X1. Therefore, as shown in FIG. 10, when the micro valve X1 is closed, the flow rate of the oil flowing out from the flow rate adjusting unit 235 is the first flow rate A1. When the micro valve X1 is open, the flow rate of the oil flowing out from the flow rate adjusting unit 235 is the second flow rate A2. By switching the opening and closing of the micro valve X1 in this way, the flow rate of the oil can be adjusted in two stages of the first flow rate A1 and the second flow rate A2.

Therefore, in the present embodiment, when the rotation speed of the compressor 14 is lower than the predetermined value, the micro valve X1 is closed. When the rotation speed of the compressor 14 is higher than the predetermined value, the micro valve X1 is opened. As a result, it is possible to prevent the oil accumulated in the oil storage chamber 205 from overflowing.

(Fourth Embodiment)
In the third embodiment, the third flow path 243 is formed in the block body 240 of the flow rate adjusting unit 235. In the present embodiment, unlike the third embodiment, as shown in FIG. 14, the third flow path 243 is not formed in the block body 240. Each of the first flow path 241 and the second flow path 242 communicates with the flow path of the micro valve X1.

Further, in the present embodiment, unlike the third embodiment, the flow path opening degree of the micro valve X1 can be changed to an arbitrary size. The method of changing the flow path opening degree of the micro valve X1 to an arbitrary size is the same as that of the second embodiment. Other than these, the configuration of the oil separator 15 is the same as that of the third embodiment.

Here, unlike the present embodiment, when the oil separator 15 does not include the flow rate adjusting unit 235, the oil return amount cannot be adjusted to a desired amount. Therefore, when the rotation speed of the compressor 14 fluctuates, the optimum oil rate cannot be maintained.

On the other hand, according to the present embodiment, by changing the opening degree of the micro valve X1, the oil return amount is changed to the first flow rate A1 and the second flow rate as shown in FIG. 11, as in the second embodiment. It can be adjusted to any size between the flow rate A2 and the flow rate A2. Therefore, the opening degree of the micro valve X1 is controlled based on the rotation speed of the compressor 14 so that the optimum oil return amount is obtained according to the rotation speed of the compressor 14. As a result, even if the rotation speed of the compressor 14 fluctuates, the oil can be returned in the optimum amount, and the optimum oil rate can be maintained.

(Fifth Embodiment)
In this embodiment, the microvalve X1 of the first embodiment is modified to have a failure detection function. Specifically, in addition to the same configuration as that of the first embodiment, the micro valve X1 includes a failure detection unit X50 as shown in FIGS. 15 and 16.

The failure detection unit X50 includes a bridge circuit formed on the arm X126 of the intermediate layer X12. The bridge circuit includes four gauge resistors connected as shown in FIG. That is, the failure detection unit X50 is a bridge circuit whose resistance changes according to the distortion of the arm X126 corresponding to the diaphragm. That is, the failure detection unit X50 is a semiconductor piezo resistance type distortion sensor. The failure detection unit X50 may be connected to the arm X126 via an electrical insulating film so as not to conduct with the arm X126.

Wiring X51 and X52 are connected to two input terminals on the diagonal of this bridge circuit. Then, a voltage for generating a constant current is applied from the wirings X51 and X52 to the input terminal. The wirings X51 and X52 branch from the voltage applied to the microvalve X1 (that is, the microvalve drive voltage) via the electrical wirings X6 and X7 and extend to the above two input terminals.

Further, the wirings X53 and X54 are connected to two output terminals on different diagonals of the bridge circuit. Then, a voltage signal at a level corresponding to the amount of distortion of the arm X126 is output from the wirings X53 and X54. As will be described later, this voltage signal is used as information for determining whether or not the microvalve X1 is operating normally. The voltage signals output from the wirings X53 and X54 are input to the control device X55 outside the microvalve X1.

The control device X55 may be, for example, an air conditioner ECU that controls the operation of a compressor, a blower, an air mix door, an inside / outside air switching door, or the like in a vehicle air conditioner. Alternatively, the control device X55 may be a meter ECU that displays the vehicle speed, the remaining fuel amount, the remaining battery amount, and the like in the vehicle.

When the control device X55 acquires a voltage signal corresponding to the amount of distortion of the arm X126 via the wirings X53 and X54, the control device X55 detects the presence or absence of failure of the microvalve X1 according to the voltage signal. Examples of the failure to be detected include a failure in which the arm X126 breaks, a failure in which a minute foreign substance is caught between the movable portion X128 and the first outer layer X11 or the second outer layer X13, and the movable portion X128 becomes immobile.

When the beam X127 and the movable portion X128 are displaced according to the expansion and contraction of the plurality of first ribs X123 and the plurality of second ribs X124, the amount of strain of the arm X126 changes. Therefore, the position of the movable portion X128 can be estimated from the voltage signal corresponding to the strain amount of the arm X126. On the other hand, if the microvalve X1 is normal, there is also a correlation between the amount of electricity supplied from the electrical wirings X6 and X7 to the microvalve X1 and the position of the movable portion X128. This energization amount is a control amount for controlling the micro valve X1.

The control device X55 utilizes this to detect the presence or absence of a failure of the microvalve X1. That is, the control device X55 calculates the position of the movable portion X128 from the voltage signals from the wirings X53 and X54 based on the predetermined first map. Then, based on a predetermined second map, the power supplied from the electric wirings X6 and X7 required to realize the position in the normal state to the microvalve X1 is calculated from the position of the movable portion X128. These first map and second map are recorded in the non-volatile memory of the control device X55. Non-volatile memory is a non-transitional substantive storage medium. The correspondence between the voltage signal level and the position in the first map may be determined in advance by an experiment or the like. Further, the correspondence relationship between the position in the second map and the supplied power may be determined in advance by an experiment or the like.

Then, the control device X55 compares the calculated electric power with the electric power actually supplied from the electric wirings X6 and X7 to the microvalve X1. Then, the control device X55 determines that the micro valve X1 is out of order if the absolute value of the difference between the former power and the latter power exceeds the permissible value, and if it does not exceed the permissible value, the micro valve It is determined that X1 is normal. Then, when it is determined that the micro valve X1 is out of order, the control device X55 performs predetermined failure notification control.

In this failure notification control, the control device X55 operates a notification device X56 that notifies a person in the vehicle. For example, the control device X55 may turn on the warning lamp. Further, the control device X55 may cause the image display device to display an image indicating that a failure has occurred in the microvalve X1. As a result, the occupant of the vehicle can notice the failure of the micro valve X1.

Further, in this failure notification control, the control device X55 may record information indicating that a failure has occurred in the microvalve X1 in the storage device in the vehicle. This storage device is a non-transitional substantive storage medium. As a result, the failure of the micro valve X1 can be recorded.

Further, when the control device X55 determines that the micro valve X1 is out of order, the control device X55 performs energization stop control. In the energization stop control, the control device X55 stops the energization from the electric wirings X6 and X7 to the microvalve X1. In this way, by stopping the energization of the micro valve X1 when the micro valve X1 fails, the safety of the micro valve X1 at the time of failure can be enhanced.

As described above, the failure detection unit X50 outputs a voltage signal for determining whether or not the microvalve X1 is operating normally, so that the control device X55 can easily determine whether or not the microvalve X1 has a failure. Can be determined.

Further, this voltage signal is a signal corresponding to the amount of distortion of the arm X126. Therefore, it is possible to easily determine whether or not the microvalve X1 has failed based on the relationship between the amount of electricity supplied from the electrical wirings X6 and X7 to the microvalve X1 and this voltage signal.

In this embodiment, it is determined whether or not the microvalve X1 is out of order based on the change in the resistance constituting the bridge circuit. However, as another method, it may be determined whether or not the microvalve X1 has failed based on the change in capacitance. In this case, instead of the bridge circuit, a plurality of electrodes forming a capacitive component are formed on the arm X126. There is a correlation between the amount of strain in the arm X126 and the capacitance between the plurality of electrodes. Therefore, the control device can determine whether or not the microvalve X1 has failed based on the change in the capacitance between the plurality of electrodes.

(Other embodiments)
(1) In the first and second embodiments, an oil flow path through which oil flows from the oil storage chamber for storing oil toward the sliding portion of the compressor is formed inside the tank 101. However, the oil flow path may be formed outside the tank 101.

(2) In the third and fourth embodiments, the oil storage chamber 205 is formed separately from the separation portion composed of the first cylinder 231 and the like. However, the oil storage chamber 205 may be formed as a part of the separation portion.

(3) In the third and fourth embodiments, the oil flow path is formed in the oil transport pipe 234 connected to the outside of the housing 201. However, the oil flow path may be formed inside the housing 201.

(4) In the third and fourth embodiments, the oil separator 15 is configured to be integrated with the compressor 14. However, the oil separator 15 may be configured as a separate body from the compressor 14.

(5) In each of the above embodiments, the plurality of first ribs X123 and the plurality of second ribs X124 are made of a semiconductor material. However, these members may be made of other materials such as a metal material that generates heat when energized and expands when its own temperature rises due to the heat generation. Further, these members may be made of a shape memory material that deforms when the temperature changes. In this case, the drive unit is displaced due to its thermal deformation.

(6) In the first embodiment or the like, when the energization from the electric wirings X6 and X7 to the microvalve X1 is stopped, the microvalve X1 is closed. However, this does not necessarily have to be the case. For example, when the energization from the electrical wirings X6 and X7 to the microvalve X1 is stopped, the microvalve X1 may be opened.

(7) The shape and size of the micro valve X1 are not limited to those shown in the above embodiment. The micro valve X1 may have a first oil hole X16 and a second oil hole X17 having a hydraulic diameter that can control a very small flow rate and do not clog minute dust existing in the flow path.

(8) The present invention is not limited to the above-described embodiment, and can be appropriately modified within the scope of the claims, and includes various modifications and modifications within the uniform range. Further, the above embodiments are not unrelated to each other, and can be appropriately combined unless the combination is clearly impossible. Further, in each of the above embodiments, it goes without saying that the elements constituting the embodiment are not necessarily essential except when it is clearly stated that they are essential or when they are clearly considered to be essential in principle. stomach. Further, in each of the above embodiments, when numerical values such as the number, numerical values, quantities, and ranges of the constituent elements of the embodiment are mentioned, when it is clearly stated that they are particularly essential, and when it is clearly limited to a specific number in principle. It is not limited to the specific number except when it is done. Further, in each of the above embodiments, when the material, shape, positional relationship, etc. of the constituent elements, etc. are referred to, except when specifically specified or when the material, shape, positional relationship, etc. are limited to a specific material, shape, positional relationship, etc. in principle. , The material, shape, positional relationship, etc. are not limited.

(summary)
According to the first aspect shown in part or all of the above embodiments, the oil return device for returning the oil to the compressor of the refrigeration cycle device is directed from the oil storage chamber for storing the oil to the sliding portion of the compressor. It is provided with a flow path forming portion for forming an oil flow path through which oil flows, and a valve component provided in the flow path forming portion for adjusting the flow rate of oil flowing through the oil flow path. The valve parts include an oil chamber through which oil flows, a base in which a first oil hole communicating with the oil chamber and a second oil hole communicating with the oil chamber are formed, and a drive unit that displaces when its own temperature changes. The amplification unit that amplifies the displacement due to the change in the temperature of the drive unit and the displacement amplified by the amplification unit are transmitted and move in the oil chamber, so that the oil hole is between the first oil hole and the second oil hole through the oil chamber. It has a movable part that switches between communication and interruption. When the drive unit is displaced due to a change in temperature, the drive unit urges the amplification unit at the urging position, so that the amplification unit is displaced with the hinge as the fulcrum, and the amplification unit is displaced at the connection position between the amplification unit and the movable unit. Bounces the moving parts. The distance from the hinge to the connection position is longer than the distance from the hinge to the urging position.

Further, according to the second aspect, the oil return device is installed between the evaporator of the refrigerating cycle device and the refrigerant suction side of the compressor, and the refrigerant sucked by the compressor is a liquid phase refrigerant and a gas phase refrigerant. Applies to accumulators that separate into and. As in the second aspect, the oil return device of the first aspect can be applied to the accumulator.

Further, according to the third aspect, the oil return device is applied to an oil separator that separates the oil contained in the refrigerant discharged from the compressor and returns the separated oil to the compressor. As in the third aspect, the oil return device of the first aspect can be applied to the oil separator.

Further, according to the fourth aspect, the valve component includes a failure detection unit that outputs a signal for determining whether the valve component is normally operating or malfunctioning. By outputting such a signal from the valve component, it is possible to easily determine whether or not the valve component has failed.

Further, according to the fifth aspect, the signal is a signal corresponding to the amount of distortion of the amplification unit. In this way, it is possible to determine the presence or absence of a failure of the valve device based on the relationship between this signal and the control amount for controlling the valve component.

Further, according to the sixth aspect, the drive unit generates heat when it is energized. The failure detection unit outputs a signal to a device that stops energization of the valve component when the valve component is out of order. In this way, by stopping the energization when the valve component fails, the safety at the time of failure can be enhanced.

Further, according to the seventh aspect, the failure detection unit outputs a signal to a device that operates a notification device that notifies a person when a valve component is out of order. Thereby, a person can know the failure of the valve component.

Further, according to the eighth viewpoint, the valve component is composed of a semiconductor chip. Therefore, the valve component can be configured in a small size.

12 Accumulator 101a Space inside the tank 103a Bottom of the outer pipe 105a Bottom of the tank body 111 Partition wall X1 Micro valve

Claims (9)

An oil return device that returns oil to the compressor of a refrigeration cycle device.
Oil flow paths (110, 112, 113, 115, XV1, XV2, 234c, 234d, 241 and 242, 243) through which oil flows from the oil storage chambers (101a, 205) toward the sliding portion of the compressor. (103a, 105a, 111, 234a, 234b, 240, X2) and
A valve component (X1) provided in the flow path forming portion and adjusting the flow rate of oil flowing through the oil flow path based on the rotation speed of the compressor is provided.
The valve parts are
A base (X11, X121, X13) in which an oil chamber (X19) through which oil flows, a first oil hole (X16) communicating with the oil chamber, and a second oil hole (X17) communicating with the oil chamber are formed. When,
The drive unit (X123, X124, X125) that displaces when its own temperature changes,
An amplification unit (X126, X127) that amplifies the displacement due to a change in the temperature of the drive unit, and
A movable portion (X128) that switches communication and cutoff between the first oil hole and the second oil hole via the oil chamber by transmitting the displacement amplified by the amplification portion and moving in the oil chamber. ) And,
When the drive unit is displaced due to a change in temperature, the drive unit urges the amplification unit at the urging position (XP2), so that the amplification unit is displaced with the hinge (XP0) as a fulcrum and the above. The amplification unit urges the movable portion at the connection position (XP3) between the amplification unit and the movable portion.
Than the distance from the hinge to the urging position, towards the distance from the hinge to the connecting position is rather long,
The oil flow path includes a first flow path (115) having a fixed flow path cross-sectional area and a second flow path (XV2, XV1) through which the oil flows by bypassing the first flow path.
The valve component is connected in the middle of the second flow path, and based on the rotation speed of the compressor, the movable portion communicates and shuts off between the first oil hole and the second oil hole. An oil return device that adjusts the flow rate of oil flowing through the oil flow path by switching to open and close the second flow path. An oil return device that returns oil to the compressor of a refrigeration cycle device.
Oil flow paths (110, 112, 113, 115, XV1, XV2, 234c, 234d, 241 and 242, 243) through which oil flows from the oil storage chambers (101a, 205) toward the sliding portion of the compressor. (103a, 105a, 111, 234a, 234b, 240, X2) and
A valve component (X1) provided in the flow path forming portion and adjusting the flow rate of oil flowing through the oil flow path based on the rotation speed of the compressor is provided.
The valve parts are
A base (X11, X121, X13) in which an oil chamber (X19) through which oil flows, a first oil hole (X16) communicating with the oil chamber, and a second oil hole (X17) communicating with the oil chamber are formed. When,
The drive unit (X123, X124, X125) that displaces when its own temperature changes,
An amplification unit (X126, X127) that amplifies the displacement due to a change in the temperature of the drive unit, and
A movable portion (X128) that switches communication and cutoff between the first oil hole and the second oil hole via the oil chamber by transmitting the displacement amplified by the amplification portion and moving in the oil chamber. ) And,
When the drive unit is displaced due to a change in temperature, the drive unit urges the amplification unit at the urging position (XP2), so that the amplification unit is displaced with the hinge (XP0) as a fulcrum and the above. The amplification unit urges the movable portion at the connection position (XP3) between the amplification unit and the movable portion.
Than the distance from the hinge to the urging position, towards the distance from the hinge to the connecting position is rather long,
The valve component not only switches communication and blocking between the first oil hole and the second oil hole by the movable portion, but also has the first movement by the movable portion based on the rotation rate of the compressor. An oil return device that adjusts the flow rate of oil flowing through the oil flow path by adjusting the opening degree of at least one of the oil hole and the second oil hole. The oil return device is installed between the evaporator of the refrigeration cycle device and the refrigerant suction side of the compressor, and is an accumulator that separates the refrigerant sucked by the compressor into a liquid phase refrigerant and a gas phase refrigerant. The oil return device according to claim 1 or 2 , which is applied to 12). The oil according to claim 1 or 2 , wherein the oil return device separates the oil contained in the refrigerant discharged from the compressor and applies the separated oil to the oil separator (15) that returns the separated oil to the compressor. Return device. The valve component is provided with a failure detection unit (X50) for outputting a signal for determining whether the valve component is operating normally or failing, according to any one of claims 1 to 4. The oil return device described. The oil return device according to claim 5 , wherein the signal is a signal corresponding to the amount of distortion of the amplification unit. The drive unit generates heat when energized and generates heat.
The oil return device according to claim 5 or 6 , wherein the failure detection unit outputs the signal to a device (X55) that stops energization of the valve component when the valve component is out of order. The fifth or sixth aspect of the present invention, wherein the failure detection unit outputs the signal to a device (X55) that operates a notification device (X56) that notifies a person when the valve component is out of order. Oil return device. The oil return device according to any one of claims 1 to 8 , wherein the valve component is composed of a semiconductor chip.

Images