JPWO2020235076A1 - Compressor and air conditioner equipped with this compressor - Google Patents

Abstract

The compressor includes an electric motor, a closed container that houses a compression mechanism portion driven by the electric motor, and an accumulator attached to the closed container, and a suction pipe of the accumulator sucks the compression mechanism portion. It is connected to the mouth side. The suction pipe of the accumulator is provided as a first suction pipe that connects the suction port side of the compression mechanism portion and the container of the accumulator, and is provided in the container of the accumulator, and is manufactured as a separate member from the first suction pipe. One end side is connected to the first suction pipe, and the other end side is provided with a second suction pipe that opens to the upper part in the container of the accumulator. In the second suction pipe, the connection portion with the first suction pipe has a circular cross-sectional shape, and at least a part of the second suction pipe has a non-circular cross-sectional shape.

Description

The present invention relates to a compressor used in refrigerating and air-conditioning equipment and an air conditioner equipped with the compressor, and is particularly suitable for a rotary type compressor in which an accumulator is attached to a closed container.

As a rotary type compressor in which an accumulator is attached to a conventional closed container, there is one described in Japanese Patent Application Laid-Open No. 2012-47075 (Patent Document 1). The compressor described in Patent Document 1 is provided with a suction pipe for supplying the gas refrigerant in the accumulator to the compression mechanism portion of the compressor. The suction pipe is composed of one L-shaped piping member, one end side thereof is connected to the suction port side of the compression mechanism portion, and the other end side is open in the accumulator. Further, in order to prevent the liquid refrigerant in the accumulator from flowing into the compression mechanism portion, the other end side of the suction pipe is opened at the upper part in the accumulator.

The L-shaped piping member has a first straight line portion extending in the radial direction (L2) from the side surface of the compressor, a curved line portion that bends substantially at a right angle from the first straight line portion, and an axial direction (L1) of the compressor from the curved line portion. It has a second straight section that extends along and opens into the accumulator. Further, in the L-shaped piping member, at least the cross section of the second straight line portion is elliptical or oval, and the elliptical or oval long axis is substantially orthogonal to the axial direction and the radial direction ( It is configured to be in line with L3).
As a result, the rigidity in the L3 direction is increased and the natural frequency is shifted to suppress the vibration of the second straight portion of the L-shaped piping member due to the rotation of the compressor.

Japanese Unexamined Patent Publication No. 2012-47075

In the case of Patent Document 1, since the L-shaped piping member has at least an elliptical or oval cross section of the second straight line portion, a hole formed in the bottom of the accumulator container through which the second straight line portion penetrates. It is also necessary to form the accumulator in accordance with the elliptical shape or the oval shape, which deteriorates the manufacturability of the accumulator and causes an increase in cost. Further, with respect to the L-shaped piping member, forming an L-shaped pipe into an elliptical shape or an oval shape is poor in manufacturability and causes an increase in cost. Further, when manufacturing the L-shaped piping member, it is necessary to consider the directionality of the elliptical shape or the oval shape of the second straight line portion with respect to the L-shaped piping member, and from this point as well, the manufacturability is as follows. Is bad and causes an increase in cost.

An object of the present invention is to obtain a compressor capable of suppressing vibration of a suction pipe in an accumulator and capable of being manufactured at low cost, and an air conditioner equipped with the compressor.

The present invention includes an electric motor, a closed container for accommodating a compression mechanism driven by the electric motor, and an accumulator attached to the closed container, and a suction pipe of the accumulator sucks the compression mechanism. In the compressor connected to the mouth side, the suction pipe of the accumulator is provided in the first suction pipe connecting the suction port side of the compression mechanism and the container of the accumulator, and in the container of the accumulator. Manufactured as a separate member from the first suction pipe, one end side is connected to the first suction pipe, and the other end side is provided with a second suction pipe that opens to the upper part in the container of the accumulator. The suction pipe is characterized in that the connection portion with the first suction pipe has a circular cross-sectional shape, and at least a part of the second suction pipe has a non-circular cross-sectional shape.

Another feature of the present invention is the compression in an air conditioner in which a compressor, a four-way valve, a heat source side heat exchanger, an expansion valve, and a utilization side heat exchanger are sequentially connected by a refrigerant pipe to form a refrigeration cycle. As a machine, it is equipped with the above compressor.

According to the present invention described above, there is an effect that a compressor capable of suppressing vibration of a suction pipe in an accumulator and can be manufactured at low cost and an air conditioner equipped with the compressor can be obtained. ..

It is a vertical sectional view which shows Example 1 of the compressor of this invention. It is a top view of the compressor shown in FIG. FIG. 1 is a cross-sectional view taken along the line AA of FIG. FIG. 1 is a cross-sectional view taken along the line BB of FIG. FIG. 1 is a cross-sectional view taken along the line CC of FIG. It is a plan view of the compressor shown in FIG. 1, and is the figure which shows only the accumulator part in the cross section seen from the position of line BB of FIG. It is a figure which shows the modification 1 of the lower side pipe part of FIG. 1, and is the figure which corresponds to FIG. 3B. It is a figure which shows the modification 2 of the lower side pipe part of FIG. 1, and is the figure which corresponds to FIG. 3B. It is a figure which shows the modification 3 of the lower side pipe part of FIG. 1, and is the figure which corresponds to FIG. 3B. It is a refrigerating cycle block diagram which shows an example of the air conditioner to which the compressor of this invention is applied. It is a vertical sectional view which shows Example 2 of the compressor of this invention. It is a cross-sectional view taken along the arrow of the DD line and the EE line of FIG. It is a vertical sectional view which shows Example 3 of the compressor of this invention. 9 is a cross-sectional view taken along the line FF of FIG. 9 is a cross-sectional view taken along the line GG of FIG. It is a vertical sectional view which shows Example 4 of the compressor of this invention. FIG. 11 is a cross-sectional view taken along the line OH of FIG. FIG. 11 is a cross-sectional view taken along the line I-I of FIG. It is a figure which shows Example 5 of the compressor of this invention, and is the figure which corresponds to FIG.

Hereinafter, specific examples of the present invention will be described with reference to the drawings. In each figure, the parts with the same reference numerals indicate the same or corresponding parts.

Hereinafter, Example 1 of the compressor of the present invention will be described with reference to FIGS. 1 to 6.
First, the overall configuration of the compressor of the first embodiment will be described with reference to FIGS. 1 and 2. FIG. 1 is a vertical cross-sectional view showing the overall configuration of the compressor 1, and FIG. 2 is a plan view of the compressor shown in FIG. In the description of the first embodiment, the case where the compressor is a single cylinder and vertical electric rotary compressor will be described, but the present invention is not limited to the single cylinder and vertical electric rotary compressor. Absent.

As shown in FIGS. 1 and 2, the compressor 1 according to the present embodiment has a configuration in which a closed container 2 and an accumulator 3 are joined by a bent steel plate support metal fitting 4.

The closed container 2 is a closed container that houses the electric motor 5 and the compression mechanism portion 6 inside. The accumulator 3 is a container provided for temporarily storing the refrigerant from the refrigerating cycle of the refrigerating and air-conditioning equipment described later and supplying it to the suction side of the compressor.

The closed container 2 is composed of a body portion 2a, a lid cap 2b, and a bottom cap 2c. The body portion 2a is made of a steel plate and has a cylindrical shape with upper and lower openings. The inside of the closed container 2 is sealed by fitting the lid cap 2b to the upper portion of the body portion 2a, fitting the bottom cap 2c to the lower portion of the body portion 2a, and welding each fitting portion. It has a structured structure.

The electric motor 5 is a drive source for driving the compression mechanism unit 6. The electric motor 5 includes a stator 5a fixed to a closed container 2 by shrink fitting or the like, and a rotor 5b fitted with a crankshaft 7 of a compression mechanism portion 6.

The compression mechanism unit 6 compresses the refrigerant and supplies it to refrigerating and air-conditioning equipment such as an air conditioner. The compression mechanism unit 6 mainly includes the crankshaft 7, main bearing 8, cylinder 9, and sub. It includes a bearing 10, a roller 11, and a vane 12.

The crankshaft 7 is a member that drives the roller 11 inside the cylinder 9. The crankshaft 7 is rotationally supported by the main bearing 8 and the sub-bearing 10. The main bearing 8 rotatably supports the intermediate portion of the crankshaft 7, and the auxiliary bearing 10 rotatably supports the lower portion of the crankshaft 7. The main bearing 8 is fixed to the body portion 2a by welding or the like.

The crankshaft 7 includes an eccentric portion 7a between the main bearing 8 and the sub-bearing 10, and the eccentric portion 7a causes the roller 11 to revolve in the cylinder 9. The roller 11 revolves in the cylinder 9 while its outer circumference abuts on the vane 12.

The cylinder 9 is fixed to the main bearing 8 by bolts (not shown). Further, the auxiliary bearing 10 is also fixed to the main bearing 8 by the bolt 13.
A refrigerating machine oil for lubricating the sliding portion of the compression mechanism portion 6 is sealed inside the closed container 2, and the refrigerating machine oil is stored on the bottom cap 2c.

The accumulator 3 is attached to the body portion 2a of the closed container 2 by a support metal fitting 4, and the support metal fitting 4 is connected to the side wall of the accumulator 3 at a position near the center in the height direction of the accumulator 3. Further, as shown in FIG. 2, the support metal fitting 4 is formed by bending a long flat steel plate into a shape that can be easily joined to the outer peripheral surface of the closed container 2 and the outer peripheral surface of the accumulator 3. , A body portion 4a and a pair of leg portions 4b. The body portion 4a is welded and fixed to the outer peripheral surface of the closed container 2, and the leg portions 4b are formed so as to project from the body portion 4a in the direction of the accumulator 3.

Further, the closed container 2 and the accumulator 3 are connected by a suction pipe 14. The refrigerant in the accumulator 3 is supplied to the suction port 15 of the compression mechanism unit 6 built in the closed container 2 via the suction pipe 14.

In this embodiment, the suction pipe 14 is formed on an L-shaped first suction pipe 14a which is a curved pipe portion connecting the suction port 15 side and the lower part of the container of the accumulator 3, and the first suction pipe. It is connected and provided inside the accumulator 3, and also includes a straight second suction pipe 14b manufactured as a separate member from the first suction pipe.
The second suction pipe 14b is arranged inside the accumulator 3 so as to extend in the vertical direction.

In the straight second suction pipe 14b of the suction pipe 14, the lower end portion 14bc on one end side thereof is connected to the first suction pipe 14a at the bottom of the container of the accumulator 3, and the upper end portion 14ba1 on the other end side is It is open at the top of the accumulator 3 or near the ceiling. In this embodiment, the upper end portion 14ba1 of the second suction pipe 14b is an unfixed free end.

An inflow pipe 16 into which the refrigerant from the refrigerating cycle of the refrigerating and air-conditioning equipment flows is provided above the accumulator 3.
On the other hand, the L-shaped first suction pipe 14a, which is a curved pipe portion, is arranged outside the lower part of the container of the accumulator 3, and one end side thereof is connected to the lower end portion 14bc of the straight second suction pipe 14b. The other end side is connected to the suction port 15 side of the compression mechanism portion 6 arranged inside the closed container 2.

In FIGS. 1 and 2, 17 is a discharge pipe for discharging the refrigerant compressed by the compressor 1, 18 is a power supply terminal, 19 is a foot of the compressor 1, and the foot 19 is a closed container 2. Three places are provided in the circumferential direction at the bottom.

Further, L2 shown in FIG. 2 indicates the radial direction connecting the center of the compressor 1 (the center of the closed container 2) and the center of the accumulator 3, and L3 connects the center of the compressor 1 and the center of the accumulator 3. The direction (circumferential direction) orthogonal to the line of the radial direction L2 is shown. The direction (circumferential direction) L3 orthogonal to the radial direction L2 is the center of the accumulator 3 in the circle L3'with the center of the compressor 1 as the center and the distance from the center of the compressor 1 to the center of the accumulator 3 as the radius. Indicates the tangential direction of.

The compressor 1 described above operates as follows.
The electric motor 5 of the compressor 1 rotates the crankshaft 7 of the compression mechanism unit 6 by rotating the rotor 5b. Along with the rotation, the eccentric portion 7a of the crankshaft 7 causes the roller 11 to move eccentrically, and the vane 12 in contact with the roller 11 reciprocates in the radial direction due to the eccentric movement of the roller 11.

With the movement of the compression mechanism unit 6, the refrigerant in the accumulator 3 flows into the second suction pipe 14b from the upper end portion 14ba1 of the second suction pipe 14b, and flows into the first suction pipe 14a and the suction port 15. Through, it is sucked into the cylinder 9 of the compression mechanism unit 6. The refrigerant sucked into the cylinder 9 is compressed by the compression mechanism unit 6 until the pressure changes from the suction pressure to the discharge pressure. The compressed refrigerant is once discharged into the closed container 2, and then discharged from the discharge pipe 17 installed in the closed container 2 into the refrigerating cycle of the refrigerating and air-conditioning equipment.

Here, a refrigerating cycle configuration of an air conditioner as an example of refrigerating and air-conditioning equipment will be described with reference to FIG. FIG. 6 is a refrigeration cycle configuration diagram showing an example of an air conditioner to which the compressor of the present invention is applied.
In the air conditioner 100, the compressor 1, the four-way valve 101, the heat source side heat exchanger 102, the expansion valve 103, and the utilization side heat exchanger 104 are sequentially connected by a refrigerant pipe to form a refrigeration cycle. Reference numeral 105 is a fan for supplying air to the heat source side heat exchanger, and 106 is a fan for supplying air to the user side heat exchanger.

A case where the room is cooled down will be described. In this case, the four-way valve 101 is switched so that the refrigerant gas from the compressor 1 flows in the direction of the heat source side heat exchanger 102, the heat source side heat exchanger 102 is a condenser, and the user side heat exchanger 104 is an evaporator. Functions as.

The high-temperature and high-pressure gas refrigerant compressed by the compressor 1 flows into the heat source side heat exchanger 102 from the four-way valve 101, exchanges heat with the outdoor air supplied from the fan 105, and condenses to become a liquid refrigerant. The condensed liquid refrigerant is depressurized by the expansion valve 103 to form a low-temperature low-pressure gas-liquid two-phase flow, which flows into the utilization-side heat exchanger 104. In the utilization side heat exchanger 104, heat is taken from the indoor air blown from the fan 106 and evaporated, and the indoor air is cooled to cool the room.

The gas refrigerant evaporated in the user-side heat exchanger 104 passes through the four-way valve 101 and then flows into the accumulator 3 of the compressor 1, and the liquid refrigerant and refrigerating machine oil contained in the refrigerant gas are stored in the bottom of the accumulator 3. The gas refrigerant in the accumulator 3 flows into the compression mechanism portion 6 of the compressor 1 from the suction pipe 14 shown in FIG. 1, and the same refrigeration cycle is repeated thereafter.

The liquid refrigerant accumulated in the accumulator 3 eventually evaporates to become a gas refrigerant, which is sucked into the compression mechanism unit 6. The refrigerating machine oil accumulated in the accumulator 3 is sucked into the compression mechanism unit 6 through a small hole (not shown) formed in the suction pipe 14.

In the heating operation, the four-way valve 101 is switched so that the refrigerant gas from the compressor 1 flows in the direction of the heat exchanger 104 on the user side, and the refrigerant flows in the opposite direction to that in the cooling operation. .. Further, the compressor 1 of the present invention can be similarly applied not only to an air conditioner as shown in FIG. 6 but also to a freezing device for cooling or freezing a showcase, a refrigerator, a freezer and the like.

Next, the structure of the accumulator 3 in the first embodiment will be described in detail with reference to FIGS. 1 to 4.
In the accumulator 3 of the present embodiment, as shown in FIG. 1, the second suction pipe 14b has an upper end portion 14ba1 side upper side pipe portion 14ba and a lower end portion 14bc connected to the first suction pipe 14a. The lower side pipe portion 14bb provided between the upper side pipe portion 14ba and the lower end portion 14bc is provided.

The cross-sectional shape of the upper side pipe portion 14ba is configured to have a circular cross-sectional shape as shown in FIG. 3A, which is a cross-sectional view taken along the line AA of FIG.
Further, the lower side pipe portion 14bb has an elliptical shape (or an oval shape) as shown in FIG. 3B, which is a cross-sectional view taken along the line BB of FIG. In FIG. 3B, X indicates a minor axis direction (a direction having a short cross-sectional length) in the elliptical lower side tube portion 14bb, and Y indicates a major axis direction (cross-sectional length) in the elliptical lower side tube portion 14bb. Indicates the long direction). In the first embodiment, the X direction is configured to be the same as the radial direction L2 connecting the center of the compressor 1 and the center of the accumulator 3 shown in FIG. 2, and the Y direction is the radial line L2. It is configured to be in the same direction as the direction L3 orthogonal to the direction.
Note that also in FIG. 3A, the lines corresponding to the lines in the X and Y directions in FIG. 3B are shown.

The lower end portion 14bc has a circular cross-sectional shape as shown in FIG. 3C, which is a cross-sectional view taken along the line CC of FIG. 1, and its diameter is an elliptical lower side tube shown in FIG. 3B. The diameter of the portion 14bb is larger than the diameter in the major axis direction. Further, one end side of the first suction pipe 14a having a circular cross-sectional shape is inserted into the inner surface of the lower end portion 14bc of the second suction pipe 14b, and the first suction pipe 14a and the second suction pipe 14b are connected to each other. .. In this embodiment, the diameter of the first suction pipe 14a and the diameter of the upper side pipe portion 14ba are configured to be the same.

As described above, in the present embodiment, the suction pipe 14 in the accumulator 3 is provided in the accumulator 3 and the L-shaped first suction pipe 14a connected to the suction port 15 of the compressor 1, and the first It is composed of a straight second suction pipe 14b connected to the suction pipe 14a. Further, the lower end portion 14bc of the second suction pipe 14b is formed into a circular cross-sectional shape, and at least a part of the second suction pipe 14b is formed into a non-circular cross-sectional shape such as an ellipse or an oval. The diameter of the lower end portion 14bc is larger than the length of the lower side pipe portion 14bb configured in the major axis direction.

Therefore, the rigidity of the second suction pipe 14b is increased with respect to the radial direction L2 of the compressor 1 and the direction (circumferential direction, tangential direction) L3 orthogonal to the radial direction to suppress the vibration or change the natural frequency. It is possible to avoid resonance. Further, since the lower end portion 14bc of the second suction pipe 14b connected to the first suction pipe 14a has a circular cross-sectional shape, its directionality is taken into consideration when manufacturing the second suction pipe 14b. It is not necessary, and at the time of assembling the accumulator 3, the direction in which the rigidity is desired to be increased in the second suction pipe 14b can be arbitrarily determined.

Therefore, as shown in Patent Document 1 described above, it is not necessary to manufacture the L-shaped piping member in consideration of the directionality as in the case where the second straight line portion of the L-shaped piping member has an elliptical shape. This makes it easier to select the direction in which the rigidity is increased during assembly.

Further, in the present embodiment, the diameter of the lower end portion 14bc is configured to be larger than the diameter in the major axis direction of the elliptical lower side pipe portion 14bb, so that the second suction pipe 14b has a diameter larger than that of the second suction pipe 14b. Even if a part of the suction pipe 14b is formed in an elliptical shape, the second suction pipe 14b can be inserted into the accumulator 3 from the lower part of the accumulator 3. Further, since the hole formed in the bottom of the container of the accumulator 3 for inserting the second suction pipe 14b can also be made into a circle having substantially the same diameter as the outer diameter of the lower end 14bc, the hole can be easily machined and the lower end is formed. Welding of the portion 14bc and the container of the accumulator 3 is also facilitated.

FIG. 4 is a plan view of the compressor 1 shown in FIG. 1, and is a view showing only a portion of the accumulator 3 in a cross section viewed from the position of line BB in FIG. As shown in FIG. 4, in this embodiment, the cross-sectional shape of the lower side pipe portion 14bb of the second suction pipe 14b is formed into an elliptical shape (or an oval shape), and the cross-sectional shape thereof is formed in the minor axis direction X (FIG. 4). 3B) is configured to be in the same direction as the radial direction L2 connecting the center of the compressor 1 and the center of the accumulator 3. Further, the elliptical lower side pipe portion 14bb is configured so that the major axis direction Y (see FIG. 3B) is the same as the direction (circumferential direction, tangential direction) L3 orthogonal to the radial direction L2. ..

That is, in the compressor 1, the compression mechanism unit 6 is driven by the rotation of the crankshaft 7, and the compression operation causes torque fluctuation in the direction of L3, which is the circumferential direction of the compressor 1. Further, by driving the compressor 1, vibration is generated in the compressor 1 in the radial direction and the like. Due to the torque fluctuation or the like, a larger excitation force acts on the second suction pipe 14b in the accumulator 3 in the circumferential direction L3 than in the radial direction L2. Therefore, the second suction pipe 14b is likely to generate a large vibration in the circumferential direction.

On the other hand, in this embodiment, the lower side pipe portion 14bb of the second suction pipe 14b is formed in an elliptical shape (or an oval shape), and the long axis direction Y thereof is the circumferential direction L3. It is configured in. Therefore, since the second suction pipe 14b can increase the rigidity in the direction of L3, which is the circumferential direction of the compressor 1, the exciting force due to the torque fluctuation of the compressor 1 acts on the second suction pipe 14b. However, the second suction pipe 14b can suppress the vibration.

In particular, in this embodiment, only the lower side pipe portion 14bb has a non-circular cross-sectional shape such as an elliptical shape, so that the second suction pipe 14b can be easily manufactured. That is, in order to make the second suction pipe 14b a non-circular cross-sectional shape, it is necessary to perform additional processing such as pressing the circular pipe shape, but the entire second suction pipe 14b is non-circular. Instead of having a cross-sectional shape, only a part has a non-circular cross-sectional shape, and other parts such as the upper side pipe portion 14ba remain in a circular pipe shape, which facilitates manufacturing.

In this embodiment, the cross-sectional shape of the lower side pipe portion 14bb is a non-circular cross-sectional shape, but the upper side pipe portion 14ba may be a non-circular cross-sectional shape. However, since the lower end portion 14bc side of the second suction pipe 14b is fixed and the upper end portion 14ba1 is a free end, a larger force (stress) acts on the lower side pipe portion 14bb, so that the lower side pipe portion 14bb is used. By increasing the rigidity of the non-circular cross-sectional shape, the vibration of the entire second suction pipe 14b can be reduced.

Further, the length of the lower side pipe portion 14bb having a non-circular cross-sectional shape (the length of the non-circular cross-sectional portion) is preferably 30 to 50% with respect to the total length of the second suction pipe 14b. .. Not only the lower side pipe portion 14bb but also the upper side pipe portion 14ba may be configured to have a non-circular cross-sectional shape.

In the above-described embodiment, an example in which at least a part of the second suction pipe 14b has an elliptical shape as an example of having a non-circular cross-sectional shape has been illustrated, but the non-circular cross-sectional shape is limited to an elliptical shape. It may be a non-circular cross-sectional shape having a major axis direction and a minor axis direction and having different rigidity in the major axis direction and the minor axis direction. Hereinafter, an example in which the non-circular cross-sectional shape is different from the elliptical shape will be described with reference to FIGS. 5A to 5C.

FIG. 5A is a diagram showing a modified example 1 of the lower side pipe portion 14bb of FIG. 1, and is a diagram corresponding to FIG. 3B. As shown in FIG. 5A, at least a part of the second suction pipe 14b (lower side pipe portion 14bb in this example) may be formed in an oval cross-sectional shape having parallel portions. Even with this configuration, the same effect as that of the elliptical cross-sectional shape shown in FIG. 3B can be obtained.

FIG. 5B is a diagram showing a modified example 2 of the lower side pipe portion 14bb of FIG. 1, and is a diagram corresponding to FIG. 3B. As shown in FIG. 5B, at least a part of the second suction pipe 14b (lower side pipe portion 14bb in this example) may be formed in a rhombic cross-sectional shape. Even if a rhombus shape is used instead of an ellipse shape or an oval shape, the rigidity in the long axis direction (longer cross-sectional shape) can be increased, so that the effect is almost the same as that of an elliptical shape or an oval cross-sectional shape. Can be obtained.

FIG. 5C is a diagram showing a modified example 3 of the lower side pipe portion 14bb of FIG. 1, and is a diagram corresponding to FIG. 3B. At least a part of the second suction pipe 14b (lower side pipe portion 14bb in this example) may be formed in a non-circular cross-sectional shape as shown in FIG. 5C. That is, in this modification 3, ribs 14bbr are provided along the longitudinal direction of the circular pipe portion, and in this example, a pair of ribs 14bbr facing each other with respect to the central axis of the pipe portion are provided. .. With this configuration, the rigidity in the direction in which the rib 14bbr is provided can be increased. Therefore, if the direction in which the rib 14bbr is provided in the lower side pipe portion 14bb is the major axis direction, the rigidity in the major axis direction can be increased in the minor axis direction. It can be larger than the rigidity (direction orthogonal to the major axis direction in the direction in which the rib 14bbr is not provided). Therefore, it is possible to obtain almost the same effect as that of forming an elliptical or oval cross-sectional shape. Further, the cross-sectional shape as shown in FIG. 5C is also included in the concept of the non-circular cross-sectional shape in the present invention.

According to the compressor of the present embodiment described above, the following effects can be obtained.
Since at least a part of the cross-sectional shape of the second suction pipe 14b is formed into a non-circular cross-sectional shape having a major axis direction and a minor axis direction and having different rigidity in the major axis direction and the minor axis direction, the major axis Since the cross-sectional coefficient in the direction can be increased and the rigidity can be increased, vibration can be suppressed. Further, by adopting a configuration having a non-circular cross-sectional shape, it is possible to avoid resonance by changing the natural frequency.

Further, the L-shaped first suction pipe 14a and the straight second suction pipe 14b installed in the container in the accumulator 3 are used as separate members, and the second suction pipe 14b is used as the L-shaped first suction pipe. It is independent of the tube 14a. Further, the connection portion of the second suction pipe 14b with the first suction pipe 14a has a circular cross section. Therefore, when assembling the accumulator 3, the long axis direction of the non-circular cross-sectional shape in the second suction pipe 14b can be set to an arbitrary direction. In particular, by aligning the long axis direction with the circumferential direction of the compressor (tangential direction of the circle L3') L3, vibration due to rotation of the electric motor can be reduced.

The non-circular cross section is at least a part of the second suction pipe 14b, and since the formation of the non-circular cross section has no direction during manufacturing, the manufacturability can be greatly improved and the cost can be reduced. it can.

Therefore, according to the present embodiment, by changing the cross-sectional shape of the second suction pipe 14b in accordance with the vibration direction to increase the rigidity in that direction, it is possible to adjust the rigidity according to the vibration direction and vibrate. It is possible to obtain a compressor that is inexpensive and has good manufacturability while suppressing noise and noise. Further, if the compressor of this embodiment is applied to an air conditioner, an air conditioner capable of reducing vibration and noise can be obtained at low cost.

Example 2 of the compressor of the present invention will be described with reference to FIGS. 7 and 8. FIG. 7 is a vertical cross-sectional view showing the second embodiment of the compressor of the present invention, and FIG. 8 is a cross-sectional view taken along the line DD and EE of FIG. In FIGS. 7 and 8, the parts having the same reference numerals as those in FIGS. 1 to 4 indicate the same or corresponding parts, and the description of the same parts is omitted and the parts different from those in the first embodiment are mainly used. Explain to.

The portion of the second embodiment different from the first embodiment is the configuration of the second suction pipe 14b in the suction pipe 14. In the case of Example 1 shown in FIG. 1, in the second suction pipe 14b provided in the container of the accumulator 3, the entire lower side pipe portion 14bb has one non-circular cross-sectional shape (elliptical cross-sectional shape). The configured example was explained. On the other hand, in the second embodiment, the lower side pipe portion 14bb of the second suction pipe 14b is composed of the first non-circular cross-section portion 14bb1, the circular cross-section portion 14bb2, and the second non-circular cross-section portion 14bb3 from the top. It is a thing. The cross-sectional shapes of the first non-circular cross-sectional portion 14bb1 and the second non-circular cross-sectional portion 14bb3 have parallel portions as shown in FIG. 8, which is a cross-sectional view taken along the line DD and EE of FIG. It is configured to have an oval cross-sectional shape, and the cross-sectional shapes of the first non-circular cross-sectional portion 14bb1 and the second non-circular cross-sectional portion 14bb3 are formed to be the same. Further, the circular cross-sectional portion 14bb2 formed between the first non-circular cross-sectional portion 14bb1 and the second non-circular cross-sectional portion 14bb3 has a circular cross-sectional shape without processing, as shown in FIG. 3A. It is configured as it is.

In this way, by having two or more non-circular cross-sections in the axial direction of the second suction pipe 14b, only the non-circular cross-sections where the rigidity should be particularly increased can be formed as non-circular cross-sections. It is possible to reduce the processing cost by reducing the range formed in. Regarding the portion formed in the non-circular cross section, the vibration in the lower end 14bc side (the portion of the second non-circular cross section 14bb3) of the second suction pipe 14b on which the largest bending stress acts and the second suction pipe 14b. It is preferable to use the abdominal portion having the maximum amplitude (the portion of the first non-circular cross-sectional portion 14bb1).

In the second embodiment as well, similarly to the first embodiment shown in FIG. 4, the minor axis direction of the oval cross-sectional shape is the same as the radial direction L2 connecting the center of the compressor 1 and the center of the accumulator 3. The major axis direction is the same as the direction L3 orthogonal to the radial direction L2. Other configurations and effects are the same as in Example 1 described above.

Example 3 of the compressor of the present invention will be described with reference to FIGS. 9, 10A and 10B. 9 is a vertical cross-sectional view showing Example 3 of the compressor of the present invention, FIG. 10A is a cross-sectional view taken along the line FF of FIG. 9, and FIG. 10B is a cross-sectional view taken along the line GG of FIG. In FIGS. 9, 10A and 10B, the parts having the same reference numerals as those in FIGS. 1 to 4 and 7 indicate the same or corresponding parts, and the same parts will be omitted from the description and the first and second embodiments will be omitted. The explanation will focus on the parts that are different from.

The portion of the third embodiment different from the first embodiment is the configuration of the second suction pipe 14b in the suction pipe 14, and in the third embodiment as well as in the second embodiment, the lower side of the second suction pipe 14b. The pipe portion 14bb is composed of a first non-circular cross-section portion 14bb1, a circular cross-section portion 14bb2, and a second non-circular cross-section portion 14bb3 from the top. Further, the cross-sectional shape of the second non-circular cross-sectional portion 14bb3 is configured to be an oval cross-sectional shape having parallel portions as shown in FIG. 10B, which is a cross-sectional view taken along the line GG of FIG. Further, the minor axis direction of the oval cross-sectional shape is configured to be the same as the radial direction L2 connecting the center of the compressor 1 and the center of the accumulator 3, and the major axis direction is relative to the radial direction L2. It is configured to be in the same direction as the orthogonal direction L3.

The portion of the third embodiment different from the second embodiment is the shape of the first non-circular cross-sectional portion 14bb1. In Example 2, an example in which the shape of the first non-circular cross-section portion 14bb1 is configured to be the same as the shape of the second non-circular cross-section portion 14bb3 has been described. Further, also in the third embodiment, as shown in FIG. 10A which is a cross-sectional view taken along the line FF of FIG. 9, the shape of the first non-circular cross-sectional portion 14bb1 is formed into an oval cross-sectional shape having a parallel portion. It is the same in that. However, in the third embodiment, the major axis direction of the oval cross-sectional shape is configured to be the same as the radial direction L2 connecting the center of the compressor 1 and the center of the accumulator 3, and the minor axis direction is set to the same direction. It is different from the second embodiment in that it is configured to be in the same direction as the direction (circumferential direction, tangential direction) L3 orthogonal to the radial direction L2.

As described in the second embodiment, the non-circular cross-section portion is formed at two or more locations (plural locations) in the axial direction of the second suction pipe 14b, and the range formed in the non-circular cross-section portion is reduced. In addition, the effect of reducing the processing cost can be obtained. Further, as in the third embodiment, the direction of the non-circular cross-sectional portion in the major axis direction (direction in which the cross-sectional length is long) is different for each non-circular cross-sectional portion, so that the second suction pipe 14b It is effective when the bending direction is partially changed.

That is, even if the bending direction is partially changed by configuring the long axis direction of each of the plurality of non-circular cross-sections to be the bending direction of each non-circular cross-section. , The effect of further reducing vibration can be obtained.
Other configurations and effects are the same as those in Examples 1 and 2 described above. The shape of the first non-circular cross-section portion 14bb1 is the same as that of the second embodiment, and the major axis direction of the second non-circular cross-section portion 14bb3 is the same as the radial direction L2 connecting the center of the compressor 1 and the center of the accumulator 3. It may be configured to be a direction, and the minor axis direction may be configured to be the same direction as the direction L3 orthogonal to the radial direction L2.

Example 4 of the compressor of the present invention will be described with reference to FIGS. 11, 12A and 12B. 11 is a vertical cross-sectional view showing Example 4 of the compressor of the present invention, FIG. 12A is a cross-sectional view taken along the line HU of FIG. 11, and FIG. 12B is a cross-sectional view taken along the line I-I of FIG. In FIGS. 11, 12A and 12B, the parts having the same reference numerals as those in FIGS. 1 to 4 and 7 indicate the same or corresponding parts, and the same parts will be omitted from the description and the first and second embodiments will be omitted. The explanation will focus on the parts that are different from.

The portion of the fourth embodiment different from the first embodiment is the configuration of the second suction pipe 14b in the suction pipe 14, and the lower side of the second suction pipe 14b in the fourth embodiment as in the second embodiment. The pipe portion 14bb is composed of a first non-circular cross-section portion 14bb1, a circular cross-section portion 14bb2, and a second non-circular cross-section portion 14bb3 from the top. Further, the cross-sectional shapes of the first non-circular cross-sectional portion 14bb1 and the second non-circular cross-sectional portion 14bb3 are FIG. 12A which is a cross-sectional view taken along the line HH of FIG. 11 and FIG. 12B which is a cross-sectional view taken along the line II. As shown in, it is configured in an oval cross-sectional shape having parallel portions. The minor axis direction of the oval cross-sectional shape is also configured to be the same as the radial direction L2 connecting the center of the compressor 1 and the center of the accumulator 3, and the major axis direction is orthogonal to the radial direction L2. It is configured to be in the same direction as L3 in the direction (circumferential direction, tangential direction).

The portion of the fourth embodiment different from the second embodiment is the shape of the first non-circular cross-section portion 14bb1 and the second non-circular cross-section portion 14bb3. In Example 2, an example in which the shape of the first non-circular cross-section portion 14bb1 is configured to be the same as the shape of the second non-circular cross-section portion 14bb3 has been described. On the other hand, in the fourth embodiment, as shown in FIGS. 12A and 12B, the cross-sectional length of the first non-circular cross-sectional portion 14bb1 in the major axis direction is changed to the cross-sectional length of the second non-circular cross-sectional portion 14bb3 in the major axis direction. It is shorter than the ellipse, and the cross-sectional length of the first non-circular cross-sectional portion 14bb1 in the minor axis direction is longer than the cross-sectional length of the second non-circular cross-sectional portion 14bb3 in the minor axis direction.

As described in the second embodiment, the processing cost is reduced by reducing the range formed in the non-circular cross-section portion by having two or more non-circular cross-section portions in the axial direction of the second suction pipe 14b. Can be obtained. Further, in the fourth embodiment, the length (width) of the non-circular cross-sectional portion in the major axis direction (longer cross-sectional length) and minor axis direction (shorter cross-sectional length) is set for each non-circular cross-sectional portion. It has a different configuration. Thereby, the length of each non-circular cross section in the major axis direction can be changed according to the force (or the amount of stress or bending generated) acting on each non-circular cross section of the second suction pipe 14b. The rigidity can be increased according to the acting force.

That is, in the second suction pipe 14b, the cross-sectional shape of the lower end portion 14bc side (the portion of the second non-circular cross-sectional portion 14bb3) of the second suction pipe 14b on which the largest bending stress acts is longer in the major axis direction. By forming the shape, the rigidity can be increased in response to the acting stress. Further, in the second suction pipe 14b, the load acting on the first non-circular cross-section portion 14bb1 which is the antinode of vibration is smaller than that of the second non-circular cross-section portion 14bb3, so that it is in the long axis direction. The cross-sectional length is shorter than the cross-sectional length of the second non-circular cross-sectional portion 14bb3 in the major axis direction.

In this way, by changing the cross-sectional length of the non-circular cross-sectional portion in the major axis direction according to the load acting on the second suction pipe 14b and the generated stress, the radial direction L2 in the second suction pipe 14b can be obtained. The rigidity of the circumferential direction L3 can be adjusted more appropriately. Therefore, it is possible to further suppress the vibration of the second suction pipe 14b. The cross-sectional length of the non-circular cross-sectional portion in the major axis direction can be easily adjusted by changing the crushing amount of the circular pipe constituting the second suction pipe 14b.

Other configurations and effects are the same as those in Examples 1 and 2 described above. The cross-sectional length of the first non-circular cross-sectional portion 14bb1 in the major axis direction is longer than the cross-sectional length of the second non-circular cross-sectional portion 14bb3 in the major axis direction, and the cross-sectional length of the first non-circular cross-sectional portion 14bb1 is in the minor axis direction. The cross-sectional length of the second non-circular cross-sectional portion 14bb3 may be shorter than the cross-sectional length in the minor axis direction.

Further, in this embodiment, the first non-circular cross-section portion 14bb1 and the second non-circular cross-section portion 14bb3 have different lengths in the major axis direction and the minor axis direction, and a plurality of non-circular cross sections having different shapes are configured. It has a part. The connection portion between the first non-circular cross-section portion 14bb1 and the circular cross-section portion 14bb2 or the upper side pipe portion 14ba, or the connection portion between the second non-circular cross-section portion 14bb3 and the circular cross-section portion 14bb2 or the lower end portion 14bc is gradually formed. The cross-sectional shape changes. However, these connecting portions are different from the concept of the first non-circular cross-section portion 14bb1 and the second non-circular cross-section portion 14bb3 in the present embodiment, and the connecting portion is the concept of the non-circular cross-section portion in the present embodiment. Is not included in. The first non-circular cross-section portion 14bb1 and the second non-circular cross-section portion 14bb3 in this embodiment are provided apart from each other via the circular cross-section portion 14bb2.

Example 5 of the compressor of the present invention will be described with reference to FIG. FIG. 13 is a diagram showing Example 5 of the compressor of the present invention, and is a diagram corresponding to FIG. In FIG. 13, the parts having the same reference numerals as those in FIGS. 1 to 4 indicate the same or corresponding parts, and the same parts will be omitted and the parts different from those in the first embodiment will be mainly described.

In the fifth embodiment as well, as in the first embodiment shown in FIG. 1, the second suction pipe 14b provided in the container of the accumulator 3 has a non-circular cross-sectional shape (elliptical shape) of the entire lower side pipe portion 14bb. It is composed of a cross-sectional shape of the shape).

In the first embodiment, as shown in FIG. 4, the cross-sectional shape of the lower side pipe portion 14bb of the second suction pipe 14b is formed into an elliptical shape, and the short axis direction X thereof is defined as the center of the compressor 1 and the accumulator. It is configured to be in the same direction as the radial direction L2 connecting the centers of 3, and its major axis direction Y is in the same direction as the direction (circumferential direction, tangential direction) L3 orthogonal to the line of the radial direction L2. It is configured as follows.

On the other hand, in the fifth embodiment, the cross-sectional shape of the lower side pipe portion 14bb of the second suction pipe 14b is the same as the elliptical shape, but the major axis direction Y is defined as the radial direction L2. It is configured to be inclined toward the inner diameter side with respect to the direction (circumferential direction, tangential direction) L3 orthogonal to the above.

In the compressor 1, the compression mechanism unit 6 is driven by the rotation of the crankshaft 7, and the compression operation causes torque fluctuations in the direction of L3, which is the circumferential direction of the compressor 1, and the torque fluctuations cause the accumulator. A large exciting force acts on the second suction pipe 14b in No. 3 in the direction of L3, which is the circumferential direction of the compressor 1. However, since the electric motor 5 is rotating, the exciting force acting on the second suction pipe 14b tends to be directed in the rotational direction of the electric motor 5 (the direction of the circle L3'in FIG. 2). That is, depending on the position, shape, size, etc. of the second suction pipe 14b, the direction of the exciting force acting on the second suction pipe 14b may be toward the inner diameter side of the tangential direction L3 of the circle L3'.

Therefore, in the fifth embodiment, as shown in FIG. 13, the lower side pipe portion 14bb of the second suction pipe 14b is formed in a non-circular cross-sectional shape, and the long axis direction Y thereof is set from the tangential direction L3. Is also configured to face the inner diameter side. The minor axis direction X of the non-circular cross-sectional shape is orthogonal to the major axis direction Y.

With this configuration, the exciting force acts even when the direction of the exciting force acting on the second suction pipe 14b is toward the inner diameter side of the tangential direction L3 of the circle L3'. Since the rigidity in the direction of vibration can be increased, a larger effect of suppressing and reducing vibration can be obtained.

Other configurations and effects are the same as in Example 1.
In the description of the fifth embodiment, the lower side pipe portion 14bb of the second suction pipe 14b having an elliptical cross-sectional shape has been described, but the oval shape shown in FIG. 5A and FIGS. 5B and 5C show. The same applies if the non-circular cross-sectional shape has a major axis direction and a minor axis direction and the rigidity differs between the major axis direction and the minor axis direction, such as the diamond shape shown and the non-circular cross-sectional shape provided with the rib 14bbr. .. Further, the present embodiment 5 may be applied to the first non-circular cross-section portion 14bb1 and the second non-circular cross-section portion 14bb3 in Examples 2 to 4 described above.

The present invention is not limited to the above-described examples, and includes various modifications. For example, in the above embodiment, an example in which the present invention is applied to a vertical electric rotary compressor with a single cylinder as a compressor has been described, but the present invention is the same for a rotary compressor and a scroll compressor having a plurality of cylinders. It can be applied to.
Further, it is possible to replace a part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment. Further, the above-described embodiment has been described in detail in order to explain the present invention in an easy-to-understand manner, and is not necessarily limited to those having all the described configurations.

1: Compressor, 2: Sealed container, 2a: Body, 2b: Lid cap, 2c: Bottom cap, 3: Accumulator, 4: Support bracket, 4a: Body, 4b: Leg, 5: Motor, 5a: Controller, 5b: Rotor, 6: Compressor, 7: Crank shaft, 7a: Eccentric, 8: Main bearing, 9: Cylinder, 10: Sub-bearing, 11: Roller, 12: Vane, 13: Bolt, 14: Suction pipe, 14a: First suction pipe, 14b: Second suction pipe, 14ba: Upper side pipe part, 14ba1: Upper end part, 14bb: Lower side pipe part, 14bb1: First non-circular cross-section part, 14bb2 : Circular cross section, 14bb3: Second non-circular cross section, 14bbr: Rib, 14bc: Lower end, 15: Suction port, 16: Inflow pipe, 17: Discharge pipe, 18: Power supply terminal, 19: Foot, L2: Radial direction, L3: Direction perpendicular to the line in the radial direction L2 (circumferential direction, tangential direction).

Claims (13)

A closed container for accommodating an electric motor, a compression mechanism driven by the electric motor, and an accumulator attached to the closed container are provided, and a suction pipe of the accumulator is connected to a suction port side of the compression mechanism. In the accumulator
The suction pipe of the accumulator is manufactured as a separate member from the first suction pipe that connects the suction port side of the compression mechanism portion and the container of the accumulator and the first suction pipe that is provided in the container of the accumulator. One end side is connected to the first suction pipe, and the other end side is provided with a second suction pipe that opens to the upper part in the container of the accumulator.
The second suction pipe has a circular cross-sectional shape at the connection portion with the first suction pipe, and at least a part of the second suction pipe has a non-circular cross-sectional shape. Characterized compressor. In the compressor according to claim 1,
The lower end of the second suction pipe is formed in a circular cross-sectional shape, and is connected to the first suction pipe at the bottom of the container of the accumulator, and the non-circular cross-sectional shape of the second suction pipe is in the long axis direction. A compressor having a short axis direction and having a shape configured such that the rigidity of the second suction pipe in the long axis direction is larger than the rigidity in the short axis direction. In the compressor according to claim 2,
A compressor characterized in that the non-circular cross-sectional shape of the second suction pipe is elliptical or oval. In the compressor according to claim 2,
The second suction pipe is an electric compressor characterized in that the diameter of the lower end portion thereof is larger than the length in the major axis direction of the portion having a non-circular cross-sectional shape. In the compressor according to claim 2,
The major axis direction of the portion having the non-circular cross-sectional shape is configured to be the direction (L3) orthogonal to the radial direction (L2) connecting the center of the compressor and the center of the accumulator. Characterized compressor. In the compressor according to claim 2,
The major axis direction of the portion having the non-circular cross-sectional shape is inclined toward the inner diameter side with respect to the direction (L3) orthogonal to the radial direction (L2) connecting the center of the compressor and the center of the accumulator. A compressor characterized in that it is configured to be oriented. In the compressor according to claim 2,
The non-circular cross-sectional portion formed in the non-circular cross-sectional shape of the second suction pipe is provided on the lower side pipe portion on the lower end side of the second suction pipe, and is provided on the lower side pipe portion of the second suction pipe. A compressor characterized in that the upper pipe portion on the upper end side has a circular cross-sectional shape. In the compressor according to claim 7,
The compressor is characterized in that the length of the non-circular cross section is 30 to 50% of the total length of the second suction pipe. In the compressor according to claim 7,
The lower side pipe portion of the second suction pipe is provided with a plurality of non-circular cross-sectional portions formed in a non-circular cross-sectional shape in the axial direction of the second suction pipe. Machine. In the compressor according to claim 9,
A compressor characterized in that the major axis direction of each of a plurality of non-circular cross-sections is configured to be a bending direction in each non-circular cross-section. In the compressor according to claim 9,
A compressor characterized in that the cross-sectional length in the major axis direction of each of a plurality of non-circular cross-sectional portions is changed according to a force acting on each non-circular cross-sectional portion. In the compressor according to any one of claims 1 to 11.
The compressor is an electric rotary compressor that is driven by an electric motor and has a crankshaft having an eccentric portion, and a roller that revolves in a cylinder due to the eccentric rotation of the eccentric portion, and compresses a refrigerant. Machine. In an air conditioner in which a compressor, a four-way valve, a heat source side heat exchanger, an expansion valve, and a user side heat exchanger are sequentially connected by a refrigerant pipe to form a refrigeration cycle.
An air conditioner comprising the compressor according to any one of claims 1 to 11 as the compressor.

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