JP6710348B1 - Compressor and air conditioner equipped with this compressor - Google Patents

Abstract

The compressor includes an electric motor, a hermetically-sealed container that houses a compression mechanism portion driven by the electric motor, and an accumulator attached to the hermetically-sealed 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 member separate from the first suction pipe that connects the suction port side of the compression mechanism section and the container of the accumulator, and is provided in the container of the accumulator, and is a member separate from the first suction pipe. And a second suction pipe having one end connected to the first suction pipe and the other end opened to an upper portion inside the container of the accumulator. The second suction pipe has a connecting portion with the first suction pipe having 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 for refrigeration and air conditioning equipment and the like, and an air conditioner equipped with this compressor, and is particularly suitable for a rotary compressor having an accumulator attached to a closed container.

As a conventional rotary compressor in which an accumulator is attached to a closed container, there is a compressor described in JP 2012-47075 A (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 pipe member, one end side of which is connected to the suction port side of the compression mechanism portion and the other end side of which opens into the accumulator. Further, in order to prevent the liquid refrigerant in the accumulator from flowing into the compression mechanism part, the other end side of the suction pipe is opened to the upper part in the accumulator.

The L-shaped pipe member includes a first straight line portion extending in a radial direction (L2) from a side surface of the compressor, a curved line portion bent substantially at a right angle from the first straight line portion, and the curved line portion extending in the axial direction (L1) of the compressor. It has a second straight portion extending along and opening into the accumulator. Further, in the L-shaped piping member, at least the second straight line section has an elliptical shape or an elliptical shape in cross section, and a major axis of the elliptical shape or an elliptical shape is substantially orthogonal to the axial direction and the radial direction ( L3).
Thus, by increasing the rigidity in the L3 direction and shifting the natural frequency, the vibration of the second straight portion of the L-shaped pipe member due to the rotation of the compressor is suppressed.

JP, 2012-47075, A

In the above-mentioned Patent Document 1, since the L-shaped pipe member has at least the second linear portion having an elliptical or oval cross section, a hole formed in the container bottom of the accumulator through which the second linear portion penetrates. Also needs to be formed in conformity with the elliptical shape or the elliptical shape, which deteriorates the manufacturability of the accumulator and causes an increase in cost. Also, regarding the L-shaped pipe member, if the L-shaped pipe is formed into an elliptical shape or an oval shape, the manufacturability is poor and the cost is increased. Further, when manufacturing the L-shaped piping member, it is necessary to manufacture the L-shaped piping member in consideration of the directionality of the elliptical shape or the elliptical shape of the second straight portion with respect to the L-shaped piping member. Is bad and causes cost increase.

An object of the present invention is to obtain a compressor that can suppress vibration of a suction pipe in an accumulator and can be manufactured at low cost, and an air conditioner equipped with this compressor.

The present invention includes an electric motor, a hermetically sealed container that internally houses a compression mechanism portion driven by the electric motor, and an accumulator attached to the hermetically sealed container, and a suction pipe of the accumulator is a suction pipe of the compression mechanism portion. In the compressor connected to the mouth side, the suction pipe of the accumulator is provided in the container of the accumulator, and the first suction pipe that connects the suction port side of the compression mechanism section and the container of the accumulator, The second suction pipe is manufactured as a separate member from the first suction pipe, has one end connected to the first suction pipe, and the other end having a second suction pipe opening to the upper part in the container of the accumulator. The suction pipe is characterized in that a connecting portion with the first suction pipe is formed into a circular cross-sectional shape, and at least a part of the second suction pipe is formed into a non-circular cross-sectional shape.

Another feature of the present invention is an air conditioner in which a compressor, a four-way valve, a heat source side heat exchanger, an expansion valve, and a use side heat exchanger are sequentially connected by a refrigerant pipe to form a refrigeration cycle. The above-mentioned compressor is installed as a machine.

According to the present invention described above, it is possible to obtain the compressor that can suppress the vibration of the suction pipe in the accumulator and can be manufactured at low cost, and the air conditioner including the compressor. ..

1 is a vertical sectional view showing a first embodiment of a compressor of the present invention. It is a top view of the compressor shown in FIG. FIG. 2 is a sectional view taken along the line AA of FIG. 1. FIG. 2 is a sectional view taken along the line BB of FIG. 1. 1. It is CC sectional view taken on the line of FIG. It is a top view of the compressor shown in FIG. 1, and is a figure which shows only the accumulator part in the cross section seen from the BB line position of FIG. It is a figure which shows the modification 1 of the lower side tube part of FIG. 1, and is a figure corresponded to FIG. 3B. It is a figure which shows the modification 2 of the lower side pipe part of FIG. 1, and is a figure corresponded to FIG. 3B. It is a figure which shows the modification 3 of the lower side pipe part of FIG. 1, and is a figure corresponded to FIG. 3B. It is a refrigeration cycle block diagram which shows an example of the air conditioner to which the compressor of this invention is applied. It is a longitudinal section showing Example 2 of a compressor of the present invention. FIG. 8 is a cross-sectional view taken along lines DD and EE of FIG. 7. It is a longitudinal section showing a 3rd example of a compressor of the present invention. FIG. 10 is a sectional view taken along line FF of FIG. 9. FIG. 10 is a sectional view taken along the line GG of FIG. 9. It is a longitudinal cross-sectional view showing Example 4 of the compressor of the present invention. FIG. 12 is a sectional view taken along the line HH of FIG. 11. FIG. 12 is a sectional view taken along the line I-I of FIG. 11. It is a figure which shows Example 5 of the compressor of this invention, and is a figure equivalent to FIG.

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

A first embodiment of the compressor of the present invention will be described below with reference to FIGS.
First, the overall configuration of the compressor according to the first embodiment will be described with reference to FIGS. 1 and 2. 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 vertical electric rotary compressor will be described, but the present invention is not limited to the single-cylinder 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 therein. The accumulator 3 is a container provided for temporarily storing a refrigerant from a refrigeration cycle of a refrigerating and air-conditioning apparatus described later and supplying the refrigerant to a suction side of a compressor.

The closed container 2 includes a body portion 2a, a lid cap 2b, and a bottom cap 2c. The body portion 2a is made of a steel plate, and is formed in a cylindrical shape having upper and lower openings. In the closed container 2, the lid cap 2b is fitted to the upper portion of the body portion 2a, the bottom cap 2c is fitted to the lower portion of the body portion 2a, and the fitting portions are welded together to hermetically seal the inside. It has been configured.

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

The compression mechanism section 6 compresses the refrigerant and supplies it to refrigerating and air-conditioning equipment such as an air conditioner. The compression mechanism section 6 has, as main elements, the crankshaft 7, the main bearing 8, the cylinder 9, and the auxiliary unit. The bearing 10, the roller 11, and the vane 12 are provided.

The crankshaft 7 is a member that drives the roller 11 inside the cylinder 9. The crankshaft 7 is rotatably supported by the main bearing 8 and the sub bearing 10. The main bearing 8 rotatably supports the middle 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 the outer periphery of the roller 11 contacts the vane 12.

The cylinder 9 is fixed to the main bearing 8 by a bolt (not shown). The sub bearing 10 is also fixed to the main bearing 8 by bolts 13.
Refrigerating machine oil for lubricating the sliding portion of the compression mechanism section 6 is enclosed in the closed container 2, and the refrigerating machine oil is stored on the bottom cap 2c.

The accumulator 3 is attached to the body 2a of the closed container 2 by a support fitting 4, and the support fitting 4 is connected to the side wall of the accumulator 3 at a position near the center of the accumulator 3 in the height direction. Further, as shown in FIG. 2, the support fitting 4 is formed by bending one long flat steel plate into a shape that is 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 toward 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 through the suction pipe 14 to the suction port 15 of the compression mechanism portion 6 built in the closed container 2.

In the present embodiment, the suction pipe 14 is connected to the suction port 15 side and the lower part of the container of the accumulator 3 by an L-shaped first suction pipe 14a serving as a curved pipe portion and the first suction pipe. A straight second suction pipe 14b is provided which is connected to the inside of the accumulator 3 and which is 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.

The straight second suction pipe 14b of the suction pipe 14 has a lower end portion 14bc which is one end side thereof connected to the first suction pipe 14a at the container bottom portion of the accumulator 3, and an upper end portion 14ba1 which is the other end side thereof. It opens in the upper part of the accumulator 3 or near the ceiling. In the present embodiment, the upper end portion 14ba1 of the second suction pipe 14b is a free end that is not fixed.

An inflow pipe 16 into which a refrigerant from a refrigerating cycle of a refrigerating and air-conditioning apparatus flows is provided above the accumulator 3.
On the other hand, the L-shaped first suction pipe 14a serving as the curved pipe portion is arranged outside the lower portion 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.

1 and 2, 17 is a discharge pipe through which the refrigerant compressed by the compressor 1 is discharged, 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 lower part in the circumferential direction.

Further, L2 shown in FIG. 2 indicates a radial direction connecting the center of the compressor 1 (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. A direction (circumferential direction) L3 orthogonal to the radial direction L2 is the center of the accumulator 3 in a circle L3′ whose center is the center of the compressor 1 and whose radius is the distance from the center of the compressor 1 to the center of the accumulator 3. Shows the tangential direction of.

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

With the movement of the compression mechanism portion 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 through the first suction pipe 14a and the suction port 15. It is sucked into the cylinder 9 of the compression mechanism section 6 via the. The refrigerant sucked into the cylinder 9 is compressed by the compression mechanism section 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 to the refrigeration cycle of the refrigeration and air conditioning equipment.

Here, the refrigeration cycle configuration of the air conditioner as an example of the refrigeration 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, a compressor 1, a four-way valve 101, a heat source side heat exchanger 102, an expansion valve 103, and a use side heat exchanger 104 are sequentially connected by a refrigerant pipe to form a refrigeration cycle. In addition, 105 is a fan which supplies air to the said heat source side heat exchanger, 106 is a fan which supplies air to the said utilization side heat exchanger.

A case where the indoor cooling operation is performed will be described. In this case, the four-way valve 101 is switched so that the refrigerant gas from the compressor 1 flows toward the heat source side heat exchanger 102, the heat source side heat exchanger 102 is a condenser, and the use side heat exchanger 104 is an evaporator. Function 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 is condensed into a liquid refrigerant. The condensed liquid refrigerant is decompressed by the expansion valve 103 to become a low-temperature low-pressure gas-liquid two-phase flow, and flows into the utilization side heat exchanger 104. In the use side heat exchanger 104, heat is taken from the room air blown from the fan 106 to evaporate, and the room air is cooled to cool the room.

The gas refrigerant evaporated in the usage-side heat exchanger 104 passes through the four-way valve 101, 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 portion of the accumulator 3. The gas refrigerant in the accumulator 3 flows into the compression mechanism section 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 into a gas refrigerant, which is sucked into the compression mechanism section 6. Refrigerating machine oil accumulated in the accumulator 3 is sucked into the compression mechanism section 6 through a small hole (not shown) formed in the suction pipe 14.

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

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

The upper side tube portion 14ba has a circular cross-sectional shape as shown in FIG. 3A which is a sectional view taken along the line AA of FIG.
Further, the cross-sectional shape of the lower side tube portion 14bb is configured in an elliptical shape (or an elliptical shape) as shown in FIG. 3B which is a cross-sectional view taken along the line BB of FIG. In FIG. 3B, X indicates the short axis direction (direction with a short cross section length) of the elliptical lower side tube portion 14bb, and Y indicates the long axis direction (cross section length of the elliptical lower side tube portion 14bb). Indicates a long direction). In the first embodiment, the X direction is configured to be the same direction 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 defined by the radial line L2. The direction L3 is orthogonal to the direction L3.
3A also shows lines corresponding to the lines in the X and Y directions in FIG. 3B.

As shown in FIG. 3C, which is a sectional view taken along the line CC in FIG. 1, the lower end portion 14bc has a circular sectional shape and its diameter is an elliptical lower side tube shown in FIG. 3B. The diameter is larger than the diameter of the portion 14bb 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. .. In this embodiment, the diameter of the first suction pipe 14a and the diameter of the upper pipe portion 14ba are the same.

As described above, in this embodiment, the suction pipe 14 of the accumulator 3 is provided in the accumulator 3 with the L-shaped first suction pipe 14a connected to the suction port 15 of the compressor 1. 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 has a circular cross-sectional shape, and at least a part of the second suction pipe 14b has a non-circular cross-sectional shape such as an ellipse or an oval. The lower end portion 14bb is configured such that the diameter of the lower end portion 14bc is larger than the length of the lower side tube portion 14bb 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 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. There is no need, and when assembling the accumulator 3, the direction in which the rigidity of the second suction pipe 14b is desired to be increased can be arbitrarily determined.

Therefore, as shown in the above-mentioned Patent Document 1, it is not necessary to manufacture the L-shaped piping member in consideration of the directionality, unlike the one in which the second straight line portion of the L-shaped piping member has an elliptical shape. It becomes easy, and it becomes possible to freely 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 tube portion 14bb, so that the second suction tube 14b has the same diameter. Even if a part is formed in an elliptical shape, the second suction pipe 14b can be inserted into the accumulator 3 from the lower portion of the accumulator 3. Also, the hole formed in the bottom of the container of the accumulator 3 for inserting the second suction pipe 14b can be formed in a circular shape having substantially the same diameter as the outer diameter of the lower end portion 14bc, so that the hole can be easily machined and the lower end can be formed. It is easy to weld the portion 14bc to the container of the accumulator 3.

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

That is, in the compressor 1, the compression mechanism 6 is driven by the rotation of the crank shaft 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, the compressor 1 also vibrates in the radial direction. Due to the torque fluctuation or the like, a larger exciting force acts on the second suction pipe 14b in the accumulator 3 in the circumferential direction L3 than in the radial direction L2. Therefore, large vibration is likely to occur in the second suction pipe 14b in the circumferential direction.

On the other hand, in the present embodiment, the lower pipe portion 14bb of the second suction pipe 14b is formed into an elliptical shape (or an elliptical shape), and the major axis direction Y thereof is the circumferential direction L3. Is configured. 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 vibration force due to the torque fluctuation of the compressor 1 acts on the second suction pipe 14b. Even so, the second suction pipe 14b can suppress vibration.

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

In addition, in the present embodiment, the cross-sectional shape of the lower side tube portion 14bb is a non-circular cross-sectional shape, but the upper side tube 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 large force (stress) acts on the lower side pipe portion 14bb, so that the lower side pipe portion 14bb is By increasing the rigidity of the non-circular cross-sectional shape, it is possible to reduce the vibration of the entire second suction pipe 14b.

The length of the lower tube portion 14bb having a non-circular cross section (the length of the non-circular cross section) is preferably 30 to 50% with respect to the entire length of the second suction tube 14b. .. Not only the lower side tube portion 14bb but also the upper side tube portion 14ba may 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 oval shape is illustrated and described, but the non-circular cross-sectional shape is limited to an oval shape. However, the shape may be a non-circular cross-section having a major axis direction and a minor axis direction and different in rigidity in the major axis direction and the minor axis direction. Hereinafter, an example of a non-circular cross-sectional shape different from an elliptical shape will be described with reference to FIGS. 5A to 5C.

FIG. 5A is a view showing a modified example 1 of the lower tube portion 14bb of FIG. 1, and is a view 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 elliptical cross-sectional shape having a parallel portion. 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 second modification of the lower tube 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 have a rhombic cross-sectional shape. Even if a rhombic shape is used instead of an elliptical shape or an elliptical shape, the rigidity in the major axis direction (long cross-sectional shape) can be increased. Can be obtained.

FIG. 5C is a diagram showing a modified example 3 of the lower tube portion 14bb of FIG. 1, and is a diagram corresponding to FIG. 3B. At least a part of the second suction pipe 14b (in this example, the lower pipe portion 14bb) may be configured to have a non-circular cross-sectional shape as shown in FIG. 5C. That is, in the third modification, ribs 14bbr are provided along the longitudinal direction of the circular pipe portion, and in this example, a pair of ribs 14bbr opposed to the central axis of the pipe portion is 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 of the lower tube portion 14bb is provided is the major axis direction, the rigidity in the major axis direction is The rigidity can be made larger than that in the direction in which the ribs 14bbr are not provided and which is orthogonal to the major axis direction. Therefore, it is possible to obtain substantially the same effect as that of the elliptical or oval cross-sectional shape. Further, a 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 this embodiment described above, the following effects can be obtained.
Since at least a part of the second suction pipe 14b has a non-circular cross-sectional shape having a major axis direction and a minor axis direction and different rigidity in the major axis direction and the minor axis direction, Since it is possible to increase the section modulus in the direction and increase the rigidity, it becomes possible to suppress vibration. Further, by adopting a configuration having a non-circular cross-sectional shape, it is possible to change the natural frequency and avoid resonance.

In addition, the L-shaped first suction pipe 14a and the straight second suction pipe 14b installed in the container in the accumulator 3 are separate members, and the second suction pipe 14b is 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 major axis direction of the non-circular cross-sectional shape of the second suction pipe 14b can be set to an arbitrary direction. In particular, by adjusting the major axis direction to the circumferential direction (tangential direction of the circle L3') L3 of the compressor, 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 non-circular cross section is not formed at the time of manufacturing, the manufacturability is significantly improved and the cost can be reduced. it can.

Therefore, according to the present embodiment, it is possible to adjust the rigidity in accordance with the vibration direction 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 obtain a compressor that is inexpensive and has good productivity while suppressing noise and noise. 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.

A second embodiment of the compressor of the present invention will be described with reference to FIGS. 7 and 8. 7 is a vertical sectional view showing a second embodiment of the compressor of the present invention, and FIG. 8 is a sectional view taken along the lines DD and EE of FIG. 7 and 8, the parts denoted by the same reference numerals as those in FIGS. 1 to 4 indicate the same or corresponding parts, and the description of the same parts will be omitted and the parts different from the first embodiment will be mainly described. Explained.

The second embodiment differs from the first embodiment in the configuration of the second suction pipe 14b in the suction pipe 14. In the first embodiment 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 constructed example has been described. On the other hand, in the second embodiment, the lower side tube portion 14bb of the second suction tube 14b is composed of the first non-circular cross section 14bb1, the circular cross section 14bb2, and the second non-circular cross section 14bb3 from the top. It is a thing. The cross-sectional shapes of the first non-circular cross section 14bb1 and the second non-circular cross section 14bb3 have parallel portions, as shown in FIG. 8 which is a cross-sectional view taken along the lines DD and EE in FIG. The first non-circular cross section 14bb1 and the second non-circular cross section 14bb3 have the same cross-sectional shape. Further, the circular cross-section 14bb2 formed between the first non-circular cross-section 14bb1 and the second non-circular cross-section 14bb3 has a circular cross-section shape without being processed, similar to that shown in FIG. 3A. It is configured as is.

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

In the second embodiment as well, as in 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. And the major axis direction is the same as the direction L3 orthogonal to the radial direction L2. Other configurations and effects are similar to those of the above-described first embodiment.

A third embodiment of the compressor of the present invention will be described with reference to FIGS. 9, 10A and 10B. 9 is a vertical sectional view showing a third embodiment of the compressor of the present invention, FIG. 10A is a sectional view taken along the line FF of FIG. 9, and FIG. 10B is a sectional view taken along the line GG of FIG. 9, 10A, and 10B, portions denoted by the same reference numerals as those in FIGS. 1 to 4 and 7 indicate the same or corresponding portions, and the description of the same portions will be omitted. The explanation will focus on the parts different from.

The third embodiment differs from the first embodiment in the configuration of the second suction pipe 14b in the suction pipe 14, and also in the third embodiment, like 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. In addition, the cross-sectional shape of the second non-circular cross-sectional portion 14bb3 is configured in an oval cross-sectional shape having a parallel portion, 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 elliptical cross-sectional shape is configured to be the same direction as the radial direction L2 that connects the center of the compressor 1 and the center of the accumulator 3, and the major axis direction is with respect to the radial direction L2. It is configured to be in the same direction as the orthogonal direction L3.

The third embodiment differs from the second embodiment in the shape of the first non-circular cross section 14bb1. In the second embodiment, an example in which the shape of the first non-circular cross section 14bb1 is the same as the shape of the second non-circular cross section 14bb3 has been described. 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 section 14bb1 is formed into an oval cross section having parallel portions. The points are the same. 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 that connects the center of the compressor 1 and the center of the accumulator 3, and the minor axis direction is The second embodiment differs from the second embodiment in that it is configured to be in the same direction as a direction (circumferential direction, tangential direction) L3 orthogonal to the radial direction L2.

As described above, the non-circular cross-section portion is configured to have two or more locations (a plurality of 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. In addition, as in the third embodiment, the non-circular cross-section portion is configured so that the direction of the major axis direction (direction having a long cross-section length) is different for each non-circular cross-section portion, so that the second suction pipe 14b is formed. It is effective in the case where the direction of partial bending changes.

That is, even if the direction of partial bending is 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. Therefore, the effect of further reducing vibration can be obtained.
Other configurations and effects are similar to those of the above-described first and second embodiments. The shape of the first non-circular cross section 14bb1 is the same as that of the second embodiment, and the major axis direction of the second non-circular cross section 14bb3 is the same as the radial direction L2 connecting the center of the compressor 1 and the center of the accumulator 3. The direction of the minor axis may be the same as the direction L3 orthogonal to the radial direction L2.

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

The fourth embodiment is different from the first embodiment in the configuration of the second suction pipe 14b in the suction pipe 14, and also in the fourth embodiment, like 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 shapes of the first non-circular cross-section 14bb1 and the second non-circular cross-section 14bb3 are cross-sectional views taken along the line H-H of FIG. 11, and cross-sectional views taken along the line I-I of FIG. 12B. As shown in, the cross section is formed into an oval shape having a parallel portion. The minor axis direction of the elliptical cross-sectional shape is also configured to be the same as the radial direction L2 that connects 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. The direction (circumferential direction, tangential direction) L3 is the same direction.

The difference between the fourth embodiment and the second embodiment is the shapes of the first non-circular cross section 14bb1 and the second non-circular cross section 14bb3. In the second embodiment, an example in which the shape of the first non-circular cross section 14bb1 is the same as the shape of the second non-circular cross section 14bb3 has been described. On the other hand, in the fourth embodiment, as shown in FIGS. 12A and 12B, the cross-sectional length in the major axis direction of the first non-circular cross section 14bb1 is set to the cross-sectional length in the major axis direction of the second non-circular cross section 14bb3. The cross-sectional length of the first non-circular cross section 14bb1 in the short axis direction is longer than the cross-sectional length of the second non-circular cross section 14bb3 in the short axis direction.

As described above, the processing cost is reduced by reducing the range formed in the non-circular cross-section so that the non-circular cross-section has two or more locations in the axial direction of the second suction pipe 14b. The effect that can reduce is obtained. In the fourth embodiment, the length (width) of the non-circular cross section in the major axis direction (long cross section length) and the short axis direction (short cross section length) is determined for each non-circular cross section. It has a different configuration. As a result, the length of each non-circular cross section in the major axis direction can be changed according to the force acting on each non-circular cross section of the second suction pipe 14b (or the generated stress or the amount of bending), The rigidity can be set according to the acting force.

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

In this way, by changing the cross-sectional length in the major axis direction of the non-circular cross-section portion 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 is changed. The rigidity in 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-section in the long axis direction can be easily adjusted by changing the crushing amount with respect to the circular pipe forming the second suction pipe 14b.

Other configurations and effects are similar to those of the above-described first and second embodiments. The cross-sectional length of the first non-circular cross section 14bb1 in the major axis direction is made longer than the cross-section length of the second non-circular cross section 14bb3 in the major axis direction, and the cross section length of the first non-circular cross section 14bb1 in the minor axis direction. The cross-sectional length may be shorter than the cross-sectional length in the minor axis direction of the second non-circular cross-section 14bb3.

In addition, in the present embodiment, the first non-circular cross section 14bb1 and the second non-circular cross section 14bb3 have different lengths in the major axis direction and the minor axis direction. Parts. The connecting portion between the first non-circular cross-section 14bb1, the circular cross-section 14bb2 and the upper tube portion 14ba, or the connecting portion between the second non-circular cross-section 14bb3 and the circular cross-section 14bb2 and the lower end 14bc respectively gradually. The cross-sectional shape changes. However, these connecting parts are different from the concept of the first non-circular cross-section part 14bb1 and the second non-circular cross-section part 14bb3 in this embodiment, and the connection part is the concept of the non-circular cross-section part in this embodiment. Not included in. In the present embodiment, the first non-circular cross section 14bb1 and the second non-circular cross section 14bb3 are provided separated from each other via the circular cross section 14bb2.

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

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

In the first embodiment, as shown in FIG. 4, the cross-sectional shape of the lower side tube portion 14bb of the second suction tube 14b is formed into an elliptical shape, and the minor axis direction X is the center of the compressor 1 and the accumulator. It is configured so as 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 in the radial direction L2. Is configured as follows.

On the other hand, in the fifth embodiment, it is the same that the cross-sectional shape of the lower tube portion 14bb of the second suction tube 14b is formed into an elliptical shape, but the major axis direction Y is a line in the radial direction L2. With respect to the direction (circumferential direction, tangential direction) L3 orthogonal to, the direction is inclined toward the inner diameter side.

In the compressor 1, the rotation of the crankshaft 7 drives the compression mechanism portion 6, and the compression operation causes a torque fluctuation in the direction of L3 which is the circumferential direction of the compressor 1, and the torque fluctuation causes the accumulator. A large vibration force acts on the second suction pipe 14b inside the compressor 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 rotation direction of the electric motor 5 (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 more toward the inner diameter side than the tangential direction L3 of the circle L3'.

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

With this configuration, even when the direction of the exciting force acting on the second suction pipe 14b is directed toward the inner diameter side from the tangential direction L3 of the circle L3′, the exciting force acts. Since the rigidity in the moving direction can be increased, a greater vibration suppression reduction effect can be obtained.

Other configurations and effects are similar to those of the first embodiment.
In addition, in the description of the fifth embodiment, the lower pipe portion 14bb of the second suction pipe 14b has an elliptical cross-sectional shape. However, in the oval shape shown in FIG. 5A, FIG. 5B, and FIG. 5C. 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, such as a rhombic shape or a non-circular cross section shape provided with ribs 14bbr, is similarly applicable. .. Further, the fifth embodiment may be applied to the first non-circular cross section 14bb1 and the second non-circular cross section 14bb3 in the above-described second to fourth embodiments.

It should be noted that the present invention is not limited to the above-described embodiments, but includes various modifications. For example, in the above-described embodiment, an example in which the present invention is applied to a vertical electric rotary compressor having a single cylinder as a compressor has been described, but the present invention is also applicable to a rotary compressor having a plurality of cylinders and a scroll compressor. Is applicable to.
Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Further, the above-described embodiments have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the configurations described.

1: Compressor, 2: Closed container, 2a: Body part, 2b: Lid cap, 2c: Bottom cap, 3: Accumulator, 4: Support metal fitting, 4a: Body part, 4b: Leg part, 5: Electric motor, 5a: Stator, 5b: rotor, 6: compression mechanism part, 7: crankshaft, 7a: eccentric part, 8: main bearing, 9: cylinder, 10: sub bearing, 11: roller, 12: vane, 13: bolt, 14: suction pipe, 14a: 1st suction pipe, 14b: 2nd suction pipe, 14ba: upper side pipe part, 14ba1: upper end part, 14bb: lower side pipe part, 14bb1: 1st 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: a direction (circumferential direction, tangential direction) orthogonal to the line in the radial direction L2.

Claims (13)

An electric motor, a hermetic container for accommodating a compression mechanism portion driven by the electric motor, and an accumulator attached to the hermetic container, and a suction pipe of the accumulator connected to a suction port side of the compression mechanism portion. In the compressor being used,
The suction pipe of the accumulator is provided in a container of the accumulator and a first suction pipe that connects a suction port side of the compression mechanism unit and a container of the accumulator, and is manufactured as a separate member from the first suction pipe. And a second suction pipe, one end side of which is connected to the first suction pipe and the other end side of which opens to an upper portion in the container of the accumulator,
In the second suction pipe, the connecting 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. Characteristic compressor. The compressor according to claim 1,
The lower end of the second suction pipe is configured to have a circular cross-section, and the second suction pipe is connected to the first suction pipe at the bottom of the accumulator. The non-circular cross-sectional shape of the second suction pipe has a longitudinal direction. And a minor axis direction, and the second suction pipe has a shape configured such that the rigidity in the major axis direction of the second suction pipe is higher than the rigidity in the minor axis direction. The compressor according to claim 2,
The non-circular cross-sectional shape of the second suction pipe is an elliptical shape or an oval shape. The compressor according to claim 2,
The second suction pipe is configured such that a diameter of a lower end portion thereof is larger than a length in a major axis direction of a portion having the non-circular cross-sectional shape. The compressor according to claim 2,
The major axis direction of the portion configured to have the non-circular cross-sectional shape is configured to be a direction (L3) orthogonal to a radial line (L2) connecting the center of the compressor and the center of the accumulator. Characteristic compressor. The compressor according to claim 2,
The major axis direction of the portion having the non-circular cross-sectional shape is inclined more toward the inner diameter side with respect to the direction (L3) orthogonal to the radial direction (L2) line connecting the compressor center and the accumulator center. A compressor characterized by being configured to be directional. The compressor according to claim 2,
The non-circular cross-section portion formed in the non-circular cross-section shape of the second suction pipe is provided in the lower side pipe portion that is the lower end side of the second suction pipe, and the non-circular cross-section portion of the second suction pipe is A compressor characterized in that an upper pipe portion on the upper end side has a circular cross-sectional shape. The compressor according to claim 7,
The length of the non-circular cross-section is 30 to 50% of the entire length of the second suction pipe. The compressor according to claim 7,
The lower side tube portion of the second suction pipe is provided with a plurality of non-circular cross-section portions formed in a non-circular cross-section shape in a plurality of locations in the axial direction of the second suction pipe. Machine. The compressor according to claim 9,
A compressor characterized in that a plurality of non-circular cross-section portions are provided with a major axis direction that is a bending direction in each non-circular cross-section portion. The compressor according to claim 9,
A compressor characterized in that the cross-sectional length in the major axis direction of each of the plurality of non-circular cross-sections is changed according to the force acting on each non-circular cross-section. 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 the cylinder by eccentric rotation of the eccentric portion, and is an electric rotary compressor that 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, a utilization 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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