JP2004092661A - Sealed electric compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a sealed compressor having a refrigerating capacity according to a change in the outside air temperature or a load. <P>SOLUTION: This sealed compressor comprises a suction passage 231 having one end substantially directly connected to an intake port 193a and the other end opened to the internal space of a sealed casing and substantially enclosed by a muffler 241. In this compressor, since an electric motor 7 is driven at two kinds or more of specified frequencies by an inverter device 212, a supercharging effect is exhibited in addition to rotating speed control, whereby the refrigerating capability according to the change in the outside air temperature or load can be obtained. Accordingly, the cooling efficiency can be improved to reduce the power consumption. <P>COPYRIGHT: (C)2004,JPO

Description

The present invention relates to a hermetic compressor used for a freezing and refrigeration apparatus and the like.

密閉 There is a strong demand for hermetic compressors used in freezers and refrigerators to have improved refrigeration capacity and lower noise.

As a conventional technique for improving the refrigeration capacity, the pressure in the cylinder at the time when the suction of the refrigerant gas is completed is set higher than the low pressure side pressure of the refrigeration cycle, thereby increasing the density of the refrigerant gas sucked into the cylinder. There is one that increases the refrigerating capacity and further improves the refrigerating capacity (for example, see Patent Documents 1 and 2).

Further, as a conventional technique for noise reduction, a suction portion for sucking refrigerant gas into a cylinder is improved in order to prevent generation of resonance noise in a closed container generated at the time of suction during a compression operation stroke. (For example, see Patent Document 3).

Hereinafter, an example of a conventional hermetic compressor for reducing noise will be described with reference to the drawings.

FIG. 38 is a longitudinal sectional view showing a conventional hermetic compressor, and FIG. 39 is a plan sectional view showing the conventional hermetic compressor of FIG.

38 and 39, the hermetic compressor 1 has a hermetic container 2 composed of a lower shell 3 and an upper shell 4. The electric compression element 5 in the vertically arranged closed container 2 is elastically supported by the coiled spring 8 on the closed container 2 such that the compression element 6 is disposed on the upper part and the electric motor 7 is disposed on the lower part.

The compression element 6 is composed of a cylinder 10, a piston 11, a crankshaft 12, a connecting rod 13, a bearing 14, a cylinder head 80, and the like provided integrally with the block 9. The electric motor 7 includes a rotor 15 and a stator 16 to which a crankshaft 12 is fixed by shrink fitting. Stator 16 is fixed to block 9 by screws. The lubricating oil 17 is stored in the lower part of the closed container 2.

{Circle over (a)} in FIG. 39 indicates the minimum distance between the inner wall surfaces of the sealed container 2 passing through the center of gravity on a plane where the cross-sectional area is substantially maximum in the horizontal cross section of the sealed container 2. In other words, the distance a between the inner wall surfaces of the sealed container 2 is the maximum distance in the direction perpendicular to the reciprocating direction of the piston 11 and the axial direction of the crankshaft 12. Symbol b denotes a distance between the inner wall surfaces of the closed container 2 which is substantially perpendicular to the same horizontal plane as the line segment of the distance a. That is, the distance b is the maximum distance between the inner wall surfaces of the sealed container 2 in the reciprocating direction of the piston 11. Symbol c represents the maximum axial distance of the crankshaft 12 from the upper surface of the inner wall of the closed casing 2 to the oil level of the lubricating oil 17.

One end of the suction pipe 18 for sucking the refrigerant gas in the closed container 2 is fixed to the block 9, and the other end is located on a plane passing through the center of the line indicated by the distance a and orthogonal to the line. Are located in This other end is arranged in the space inside the closed container 2 as an open end 18 a and communicates with the space inside the cylinder 10.

The operation of the conventional hermetic compressor configured as described above will be described below.

(4) Refrigerant gas circulated from a system such as a freezer / refrigerator is once released into the space inside the closed container 2, is drawn into the cylinder 10 through the suction pipe 18 fixed to the block 9, and is compressed by the piston 11. At that time, the refrigerant gas is sucked into the cylinder 10 by １ ／ rotation of the crankshaft 12 and is compressed by the subsequent 回 転 rotation.

Since the refrigerant gas is not continuously sucked into the cylinder 10 as described above, pressure pulsation of the refrigerant gas occurs in the suction pipe 18. Accordingly, the pressure pulsation vibrates the space in the closed container 2, and the resonance mode is generated in the reciprocating direction of the piston 11, the direction perpendicular to the reciprocating direction on the horizontal plane including the reciprocating direction of the piston 11, and the axial direction of the crankshaft 12. Occurs.

However, the suction end of the opening end 18a of the space inside the closed container 2 of the suction pipe 18 passes through the center of the line indicated by the distance a and is perpendicular to the line, that is, in the horizontal plane including the reciprocating direction of the piston 11. It is arranged on a plane including the position of the node of the resonance mode generated in a direction perpendicular to the direction.

Therefore, in the conventional hermetic compressor shown in FIGS. 38 and 39, the pressure pulsation vibrates the node in the resonance mode. For this reason, in the conventional hermetic compressor, the resonance mode is not excited, the generation of the resonance sound is prevented, and the noise due to the resonance sound is suppressed.

If the resonance mode of the resonance frequency in question is in the reciprocating direction of the piston 11 of the closed container 2, the opening end 18a of the space inside the closed container 2 of the suction pipe 18 is arranged at the following position. In FIG. 39, the opening end 18a is a distance between the inner wall surfaces of the sealed container 2 which is substantially perpendicular to the line segment A on the same horizontal plane as the line segment A indicated by the distance a at which the distance passing through the center of gravity of the horizontal cross section becomes minimum. A line segment B indicated by b is disposed on a plane passing through the center of the line segment B and orthogonal to the line segment B. As a result, the pressure pulsation is vibrated at the node of the resonance mode. Therefore, the resonance mode is not excited, and the generation of resonance sound can be suppressed, and the noise of the hermetic compressor due to the resonance sound is suppressed.

When the resonance mode of the resonance frequency in question is in the axial direction of the crankshaft 12 of the closed casing 2, the opening end 18a of the space inside the closed casing 2 of the suction pipe 18 is arranged at the following position. In other words, the opening end is different from the line segment C indicated by the distance c (FIG. 38) that is the maximum distance between the upper surface of the inner wall in the vertical direction of the sealed container 2 and the oil level of the lubricating oil 17. Are arranged on a plane that passes through the center of As a result, the pressure pulsation is vibrated at the node of the resonance mode. Therefore, the resonance mode is not excited, and the generation of resonance sound can be suppressed, and the noise of the hermetic compressor due to the resonance sound is suppressed.

Next, an example of a conventional hermetic compressor with an improved refrigeration capacity will be described with reference to the drawings.

FIG. 40 is a longitudinal sectional view showing a conventional hermetic compressor in which the refrigerating capacity is improved. FIG. 41 is a plan sectional view of the conventional hermetic compressor shown in FIG. FIG. 42 is a cross-sectional view of a principal part taken along line AA of FIG. FIG. 43 is an explanatory diagram of the behavior of the refrigerant gas.

In FIGS. 40, 41, 42 and 43, the valve plate 19 has a suction hole 19a and is disposed on the end face of the cylinder 10. The suction hole 19a (FIGS. 41 and 42) communicates the suction pipe 21 with the inside of the cylinder 10. The suction lead 20 shown in FIG. 42 opens and closes the suction hole 19 a of the valve plate 19. One end 21 a of the suction pipe 21 is open to the space inside the closed container 2, and the other end 21 b is directly connected to the valve plate 19.

On the other hand, in the conventional rotary compressor for improving the refrigerating capacity shown in Patent Document 1, the length L (m) of the suction pipe 21 is such that the suction stroke cycle is T (sec) and the suction of the refrigerant gas to be sucked is performed. When the sound velocity in the state is a (m / sec),
(T × a / 4−0.2) ± 0.1 = L
It becomes.

Next, the operation of the conventional hermetic compressor configured as described above will be described.

に お い て Referring to FIG. 39, at the start of the suction stroke of the refrigerant gas (at the time point (a) in FIG. 43), the suction holes 19a of the valve plate 19 are closed. For this reason, the flow of the refrigerant gas has stopped.

Next, the piston 11 moves to the right, and the volume in the cylinder 10 increases rapidly. Accordingly, a pressure difference is generated between the space inside the cylinder 10 and the space inside the closed container 2, and the refrigerant gas starts flowing rightward (toward the cylinder 10) through the suction pipe 21. At the same time, a pressure wave Wa is generated in the cylinder 10 due to a sudden increase in the volume in the cylinder 10. The pressure wave Wa in the cylinder 10 propagates through the suction pipe 19a, which is an opening, in the suction pipe 21 toward the space in the closed vessel 2 in a direction opposite to the flow of the refrigerant gas ((b in FIG. 43). ))).

(4) The pressure wave Wa that has reached the space inside the closed container 2 becomes a reflected wave Wb that is inverted in the space inside the closed container 2 where the refrigerant gas is stagnant. The reflected wave Wb propagates in the suction pipe 21 in the same direction as the flow of the refrigerant gas (at the time point (c) in FIG. 43).

That is, the pressure wave Wa generated in the cylinder 10 propagates through the suction hole 19a of the valve plate 19 in the direction opposite to the flow of the refrigerant gas. Then, the pressure wave Wa becomes a reflected wave Wb whose phase is inverted in the space inside the closed container 2, propagates in the forward direction with the flow of the refrigerant gas, and returns to the suction hole 19 a of the valve plate 19.

By making the time when the reflected wave Wb reaches the suction hole 19a coincide with the time when the volume in the cylinder 10 is maximized (the time when the suction is completed), the pressure energy of the reflected wave Wb at the time when the suction is completed is reduced to the refrigerant gas. , The suction pressure of the refrigerant gas increases.

As a result, the cylinder 10 is filled with a refrigerant gas having a higher density, the amount of refrigerant discharged per compression stroke increases, the amount of refrigerant circulation increases, and the refrigeration capacity of the hermetic compressor increases. Had improved.
JP-A-57-122192 JP-A-6-50262 JP-A-6-74154

However, in the configuration of the conventional hermetic compressor, when the temperature of the refrigerant gas changes due to a change in outside air temperature and the speed of sound transmitted through the refrigerant gas (hereinafter, referred to as the sound speed in the refrigerant gas) changes, resonance occurs. There is a possibility that the position of the node in the resonance mode of the frequency changes, and it becomes impossible to suppress the generation of the resonance sound.

Also, the impact sound generated by the pressure wave generated by the suction pipe could generate noise.

場合 Also, when the temperature of the refrigerant gas changes due to a change in the outside air temperature and the sound speed in the refrigerant gas changes, the wavelength of the pressure wave or the reflected wave changes depending on the sound speed. For this reason, an error occurs in the timing of adding the pressure energy of the reflected wave at the time of the completion of the suction, and the rate of increase of the suction pressure decreases.

Therefore, it is difficult to fill the cylinder with high-density refrigerant gas, and the amount of refrigerant gas discharged per compression stroke may be reduced, and the refrigeration capacity may be reduced.

方法 Also, a method is conceivable in which the amount of circulating refrigerant gas is constantly increased irrespective of changes in the outside temperature to improve the refrigeration capacity. However, in this case, the room is often closed in winter or the like where the outside temperature is low, and there is a possibility that the noise due to the impact sound may be more annoying than in summer.

An object of the present invention is to solve the above-mentioned problems, and an object of the present invention is to provide a hermetic compressor having a high refrigeration capacity, a small suction loss of refrigerant gas, and a high refrigeration efficiency. .

密閉 The hermetic compressor of the present invention achieves the above object in various embodiments described below.

(5) In the conventional configuration, there is a problem in the followability of the valve mechanism, and there is a possibility that the refrigeration capacity proportional to the increase in the number of rotations may not be obtained, particularly in a high rotation region.

Therefore, in a later-described first embodiment of the present invention, one end of the suction passage is substantially directly connected to the suction hole, and the other end is opened in the space in the closed container and substantially enclosed in the muffler. And the electric motor is driven at two or more specific frequencies by an inverter device. In addition, supercharging is performed in addition to the rotation speed control, particularly in a high rotation speed region, so that a refrigerating capacity greater than the capacity proportional to the rotation speed is obtained. Thereby, in the hermetic compressor of the first embodiment, a refrigerating capacity according to the outside air temperature and the load is obtained, and the power consumption is small.

Further, the hermetic compressor of the present invention reduces the pulsation of the refrigerant gas to reduce the force for exciting the refrigerant gas in the closed container, and the resonance sound is always generated regardless of the resonance frequency of the refrigerant gas in the closed container. Become smaller.

In the conventional configuration, since the open end of the suction flow path is opened in the closed vessel, when the pressure wave is reflected at the open end of the suction flow path, the refrigerant gas in the closed vessel is vibrated to generate resonance. Could produce a sound.

Therefore, in a second embodiment of the present invention described later, the pulsation of the suction gas is reduced, and the force for exciting the refrigerant gas in the closed container is reduced. Thus, the hermetic compressor can always reduce the resonance sound regardless of the resonance frequency of the refrigerant gas in the hermetic container.

In the second embodiment, the pressure amplitude is always prevented from attenuating when the pressure wave is reflected at the opening end of the suction passage regardless of the resonance frequency of the refrigerant gas in the closed vessel. For this reason, in the hermetic-type compressor, the suction pressure of the refrigerant gas always rises irrespective of all changes in the shape of the hermetic container, operating conditions, and the like, and a stable improvement in refrigeration capacity can be obtained.

Further, in the second embodiment, the temperature distribution of the suction flow path of the suction pipe is made uniform by surrounding the suction pipe with the suction muffler, thereby reducing the change in sound speed in the refrigerant gas. For this reason, the hermetic compressor can reduce the attenuation of the pressure wave and obtain a stable increase in the suction pressure. Therefore, a hermetic-type compressor capable of stably improving the refrigerating capacity can be obtained.

In the conventional configuration, the rotational position of the crankshaft when the reflected wave returns to the suction hole is not always optimal depending on the length of the suction pipe 21, the operating frequency, and the speed of sound in the refrigerant gas. Therefore, the improvement rate of the refrigerating capacity may be small.

Therefore, in a third embodiment of the present invention described later, the length of the suction pipe and the like are adjusted so that the rotational position (crank angle) of the crankshaft at which the reflected wave returns to the suction hole is optimized. Thus, a hermetic-type compressor that can obtain the minimum refrigeration capacity improvement effect is obtained.

In the conventional configuration, when the resonance frequency of the refrigerant gas in the closed container approaches an integral multiple of the number of revolutions of the crankshaft, a resonance sound is generated and the refrigerant gas in the closed container resonates. Therefore, when the pressure wave is reflected at the open end of the suction pipe, the refrigerant gas in the closed container resonates. Under the influence, there is a disadvantage that the pressure amplitude of the reflected wave decreases, the rate of increase of the suction pressure decreases, and the effect of improving the refrigerating capacity tends to decrease.

Therefore, in a fourth embodiment of the present invention described later, the resonance frequency of the refrigerant gas in the closed container is configured not to be close to an integral multiple of the rotation speed of the crankshaft. This prevents the occurrence of resonance and prevents the pressure amplitude from attenuating when the pressure wave is reflected at the opening of the suction pipe. Accordingly, a hermetic compressor in which the suction pressure is constantly increased and the effect of improving the refrigerating capacity can be obtained.

In the conventional configuration shown in FIG. 42 described above, the suction pipe 21 is in contact with the cylinder head 80 and the valve plate 19. Therefore, the temperature of the cylinder head 80 and the like greatly increases with the lapse of time after the start, and the temperature of the suction pipe 21 follows. As a result, the temperature of the refrigerant gas in the suction pipe 21 increases, the speed of sound in the refrigerant gas changes, and the timing at which the reflected wave reaches the suction hole 19a is shifted. As a result, there is a possibility that a stable suction pressure increasing effect cannot be obtained with the conventional hermetic compressor.

Therefore, in a later-described fifth embodiment of the present invention, even if the temperature of the cylinder head or the like greatly changes, the temperature change of the suction pipe is reduced. As a result, the change in sound speed in the refrigerant gas can be reduced, and a stable suction pressure increasing effect is generated. Therefore, it is possible to obtain a hermetic-type compressor having a stable high refrigeration capacity without being affected by the lapse of time after startup.

In the conventional configuration shown in FIG. 42, since the open end 21 a of the suction pipe 21 is disposed in the closed container 2, the refrigerant gas having a high temperature and a low density is sucked into the suction pipe 21. For this reason, the speed of sound in the refrigerant gas is high, the influence of compressibility is reduced, and the generation of pressure waves is weakened. Therefore, in the conventional hermetic compressor, the suction pressure may decrease.

If the open end 21a of the suction pipe 21 is communicated with the open end of the second suction pipe in the closed vessel 2 in order to suck the low-temperature refrigerant gas into the cylinder 10, a reflected wave is generated. And the suction pressure could not be increased.

In a sixth embodiment of the present invention described below, a large pressure wave is generated to increase the suction pressure increasing effect, and a low-temperature refrigerant gas is sucked into the cylinder. Thereby, the effect of improving the amount of circulating refrigerant by the refrigerant gas having a low temperature is added, the effect of improving the refrigerating capacity is greatly increased, the refrigerating capacity is increased, and a hermetic compressor with low noise is obtained.

In the conventional configuration shown in FIG. 42, when the speed of sound in the refrigerant gas changes due to a change in operating conditions, if the length of the suction pipe 21 is constant, until the reflected wave reaches the suction hole 19a of the valve plate 19, Time changes. Therefore, there is a possibility that the suction timing to the cylinder 10 is shifted, and depending on the operating conditions, the effect of increasing the suction pressure is greatly reduced and the refrigeration capacity becomes insufficient.

Therefore, in a later-described embodiment 7 of the present invention, the suction pressure is constantly increased irrespective of a change in the operating conditions, and a stable high refrigeration capacity is supplied.

(4) In the conventional configuration, since the long suction flow path is provided in the limited closed container, the structure of the suction flow path is complicated and has a plurality of bent portions having different curvatures. Therefore, when the pressure wave Wa and the reflected wave Wb propagate through the suction passage, the amplitude of the pressure is reduced at the bent portions having different curvatures. Further, when the reflected wave Wb returns to the suction hole of the valve plate, the pressure amplitude of the reflected wave Wb is attenuated, and the conventional hermetic compressor may not be able to obtain a high refrigerating capacity improvement effect.

Therefore, in an eighth embodiment of the present invention described later, the attenuation of the pressure amplitude of the pressure wave Wa and the reflected wave Wb is reduced, and the suction pressure is increased. For this reason, a hermetic compressor having a high improvement in refrigeration capacity can be obtained.

に お い て In the conventional configuration, the suction passage receives heat from the high-temperature refrigerant gas in the closed container, and the temperature of the suction passage rises, and the temperature of the suction gas in the suction passage rises. For this reason, the density of the sucked refrigerant gas becomes small, and the amount of circulating refrigerant tends to decrease.

Therefore, in a ninth embodiment of the present invention described later, the amount of heat that the suction passage receives from the high-temperature refrigerant gas in the closed container is reduced. As described above, the rise in the temperature of the suction passage is reduced, and the rise in the temperature of the refrigerant gas in the suction passage is reduced. Therefore, it is possible to obtain a hermetic compressor capable of obtaining a large amount of refrigerant circulation.

Further, in the ninth embodiment, the temperature of the refrigerant gas to be sucked is low, and the high-density refrigerant gas is sucked into the suction passage. Accordingly, the speed of sound in the refrigerant gas to be sucked is reduced, and the compressibility of the refrigerant gas is increased. For this reason, a large-sized pressure wave is generated, and a hermetic compressor in which a high improvement in refrigeration capacity is obtained can be obtained.

In the conventional configuration shown in FIG. 42, the suction pipe 21 as the suction flow passage is almost directly connected to the valve plate 19. For this reason, in the conventional hermetic compressor, the noise generated due to the pulsation of the suction gas near the suction hole 19a is transmitted through the suction flow path without much attenuation, and finally transmitted to the outside of the closed vessel 2. There was a possibility that the noise would increase.

Therefore, in a tenth embodiment of the present invention described later, the noise generated due to the pulsation of the sucked refrigerant gas is attenuated without reducing the refrigerating capacity. For this reason, the hermetic compressor of the tenth embodiment is a compressor with low noise.

In the conventional configuration, as shown by Wb in FIG. 45, when the reflected wave returns to the inside of the cylinder 10, the suction lead 20 is arranged at an angle nearly perpendicular to the traveling direction of the reflected wave. Therefore, most of the reflected waves are reflected by the suction lead 20 at an angle close to vertical. Therefore, the pressure energy of the reflected wave is not effectively transmitted to the inside of the cylinder 10, and the supercharging effect on the refrigerant gas by the reflected wave cannot be sufficiently obtained, and the refrigeration capacity may not be sufficiently improved.

Therefore, in an eleventh embodiment of the present invention described later, when the reflected wave returns to the inside of the cylinder, the reflected wave is hardly obstructed by the reflection by the suction lead, and the pressure energy of the reflected wave is effectively entered into the cylinder. . For this reason, the hermetic-type compressor of Embodiment 10 has a large refrigeration capacity.

The above conventional configuration can always provide a large refrigeration capacity regardless of whether the outside air temperature is high or low. For this reason, in the conventional hermetic compressor, at a low outside air temperature that does not require a large refrigeration capacity, an excessive refrigeration capacity is supplied, and the efficiency of the entire refrigeration system including the hermetic compressor is reduced. As a result, the total power consumption may increase.

Therefore, in later-described embodiments 12 and 13 of the present invention, a large refrigeration capacity is not obtained at a low outside temperature where a large refrigeration capacity is not required, so that the power consumption is suppressed to be small. At high outside temperatures that require capacity, the system is configured to exhibit the same large refrigeration capacity as before. For this reason, by controlling the refrigeration capacity, a hermetic compressor with a small total power consumption can be obtained.

The hermetic-type compressor of the present invention includes a suction passage that has one end substantially directly connected to the suction hole and the other end opened to a space in the closed container and substantially wrapped in the muffler. The motor is driven at two or more specific frequencies by an inverter device, and by increasing the pressure in the cylinder at the time when the suction of the refrigerant gas is completed to be higher than the low pressure side pressure of the refrigeration cycle, A high refrigerating capacity can be exhibited by the supercharging effect of increasing the density of the refrigerant gas sucked into the cylinder. Then, in order to obtain a refrigerating capacity greater than the capacity in proportion to the rotational speed, in particular in the high rotational speed region, by performing supercharging in addition to the rotational speed control, the refrigerating capacity according to the outside temperature and the load is obtained. In addition, the hermetic-type compressor of the present invention can prevent the generation of resonance noise generated at the time of suction during the compression operation, and can suppress the generation of noise.

The hermetic compressor according to claim 1 of the present invention comprises:
A compression element for compressing the refrigerant and an electric motor for driving the compression element are housed in the closed container. The compression element includes a suction muffler, a cylinder, a suction hole communicating with the cylinder, and one end of the suction hole. And a suction flow path substantially open to the space in the closed container at the other end and substantially wrapped in the muffler, wherein the electric motor is driven by an inverter at two or more specific frequencies. It is driven.

Thus, in the hermetic compressor of the present invention, by performing supercharging in addition to controlling the number of revolutions, a refrigerating capacity according to the outside air temperature and the load can be obtained, and the power consumption can be reduced.

Further, the hermetic compressor of the present invention reduces the pulsation of the suction gas to reduce the force for exciting the refrigerant gas in the closed container, and always produces a resonance sound regardless of the resonance frequency of the refrigerant gas in the closed container. Can be reduced.

At the same time, the hermetic compressor of the present invention prevents the pressure amplitude from attenuating when the pressure wave is reflected at the opening of the suction flow path, regardless of the resonance frequency of the refrigerant gas in the hermetic container, and reduces the shape of the hermetic container. Irrespective of any changes in the operating conditions and the like, the suction pressure always rises, and a stable high refrigeration capacity can be obtained.

Further, the hermetic-type compressor of the present invention can obtain a stable suction pressure increase by reducing the pressure wave attenuation by making the temperature distribution of the suction passage uniform and reducing the change in the sound velocity in the refrigerant gas. And a stable refrigeration capacity can be obtained.

The hermetic compressor according to claim 2 of the present invention comprises:
In the closed container, a compression element for compressing the refrigerant and an electric motor for driving the compression element are housed, and the compression element is a suction muffler, a cylinder, a piston reciprocating in the cylinder, and an end face of the cylinder. A valve plate disposed and having a suction hole communicating with the inside of the cylinder, one end of which is substantially directly connected to the suction hole, and the other end of which is open to a space in the closed container and substantially inside the muffler. And an enclosing suction flow path, wherein the electric motor is driven at two or more specific frequencies by an inverter device.

Thereby, in the hermetic compressor of the present invention, in the reciprocating compressor, by performing supercharging in addition to controlling the rotation speed, a refrigerating capacity according to the outside temperature and the load is obtained, and the power consumption is reduced. Can be reduced.

Further, the hermetic compressor of the present invention reduces the pulsation of the suction gas to reduce the force for exciting the refrigerant gas in the closed container, and always produces a resonance sound regardless of the resonance frequency of the refrigerant gas in the closed container. Can be reduced.

At the same time, the hermetic compressor of the present invention prevents the pressure amplitude from attenuating when the pressure wave is reflected at the opening of the suction flow path, regardless of the resonance frequency of the refrigerant gas in the hermetic container, and reduces the shape of the hermetic container. Irrespective of any changes in the operating conditions and the like, the suction pressure always rises, and a stable high refrigeration capacity can be obtained.

Furthermore, in the hermetic compressor of the present invention, by surrounding the suction pipe with a suction muffler, the temperature distribution in the suction flow path of the suction pipe is made uniform, and the change in sound speed in the refrigerant gas is reduced, thereby reducing the attenuation of the pressure wave. A small and stable increase in suction pressure can be obtained, and a stable refrigeration capacity can be obtained.

The hermetic compressor according to claim 3 of the present invention comprises:
In the closed container, a compression element for compressing the refrigerant and an electric motor for driving the compression element are housed, and the compression element is a suction muffler, a cylinder, a piston reciprocating in the cylinder, and an end face of the cylinder. A valve plate disposed and having a suction hole communicating with the inside of the cylinder, and a suction flow passage having one end practically directly connected to the suction hole and the other end opening into the suction muffler; Driven at two or more specific frequencies by the inverter device, the refrigerating capacity changes, and the pressure wave near the suction hole becomes a reflected wave at the opening end of the suction flow passage through the suction flow passage. By increasing the refrigerating capacity by increasing the refrigerant suction density by causing the reflected wave to reach the suction hole at the time of completion of suction, the range of the refrigerating capacity is expanded. Than it is.

Thereby, in the hermetic compressor of the present invention, in the reciprocating compressor, by performing supercharging in addition to controlling the rotation speed, a refrigerating capacity according to the outside temperature and the load is obtained, and the power consumption is reduced. Can be reduced.

Further, the hermetic compressor of the present invention reduces the pulsation of the refrigerant gas to reduce the force for exciting the refrigerant gas in the closed container, and the resonance sound is always generated regardless of the resonance frequency of the refrigerant gas in the closed container. Become smaller.

Further, according to the hermetic compressor of the present invention, regardless of the resonance frequency of the refrigerant gas in the hermetic container, the pressure amplitude is always prevented from being attenuated when the pressure wave is reflected at the opening of the suction flow passage, and Irrespective of any changes in the shape, operating conditions, etc., the suction pressure is always increased, and the effect of improving the refrigerating capacity can be obtained.

The closed type compressor according to claim 4 of the present invention comprises:
A suction lead for opening and closing the suction hole;
The crank angle at which the suction lead starts to open is θs (rad), the length of the suction passage is L (m), the rotation speed of the crankshaft is f (Hz), and the refrigerant in the suction passage is The sound velocity of the gas is assumed to be As (m / sec), and the return crank angle θr (rad) of the pressure wave generated in the suction hole at the start of suction, expressed by the following (Equation 1), is in the range of the following (Equation 2). It is comprised in.

θr = θs + 4π × L × f / As (1)
1.4 (rad) ≦ θr ≦ 3.0 (rad) (2)
Thereby, in the hermetic compressor of the present invention, since the suction flow path length and the like are adjusted so that the crank angle at which the reflected wave returns to the suction hole is optimized, the suction pressure is increased and the maximum The effect of improving the refrigerating capacity can be obtained.

The hermetic compressor according to claim 5 of the present invention comprises:
The resonance frequency of the refrigerant gas in the closed vessel is different from a frequency around an integral multiple of the rotation speed of the crankshaft.

Accordingly, the hermetic compressor of the present invention is configured such that the resonance frequency of the refrigerant gas in the hermetic container does not become close to an integral multiple of the number of revolutions of the crankshaft. It is possible to prevent the pressure amplitude from attenuating when the wave is reflected at the opening of the suction flow path, to constantly increase the suction pressure, and to obtain the effect of improving the refrigerating capacity.

The hermetic compressor according to claim 6 of the present invention comprises:
At least a part of the suction channel is formed of a material having low thermal conductivity.

Accordingly, the hermetic compressor of the present invention prevents the heat from the cylinder head from being conducted to the suction flow path even if the temperature of the cylinder head or the like greatly changes with the lapse of time after the start, and prevents the suction. By reducing the temperature change in the flow path, the change in the speed of sound in the refrigerant gas can be reduced, causing a stable increase in suction pressure and obtaining a stable high refrigeration capacity without being affected by the lapse of time after startup. be able to.

The hermetic compressor according to claim 7 of the present invention comprises:
The suction passage has a first suction pipe, and the second suction pipe has one end connected to the refrigeration cycle and the other end arranged as an open end near the open end of the first suction pipe. It is a thing.

Thereby, in the hermetic compressor of the present invention, by sucking the refrigerant gas having a low temperature and a high density into the suction passage, the speed of sound in the refrigerant gas is reduced, and the influence of the compressibility is increased. A large pressure wave is generated. As a result, the hermetic compressor of the present invention can increase the effect of increasing the suction pressure, and can also significantly increase the effect of improving the refrigerating capacity by sucking the low-temperature refrigerant gas into the cylinder. And the transmission of pressure pulsation from the second suction pipe to the refrigeration cycle can be reduced, and noise can be reduced.

The hermetic compressor according to claim 8 of the present invention comprises:
The suction passage has a plurality of open ends, and has at least two types of lengths from the suction hole to the open end.

Thus, in the hermetic compressor of the present invention, the generated pressure wave is reflected at each open end of the suction flow path and reaches the suction hole, so that the timing of the reflected wave reaching the suction hole is widened. be able to.

Therefore, in the hermetic compressor of the present invention, the sound speed in the refrigerant gas changes due to a change in operating conditions and the like, and even if the timing at which one reflected wave arrives at the suction hole is shifted, other reflected waves are successively generated. A high pressure refrigerant gas can always be supplied into the cylinder to reach the suction hole. As a result, the hermetic compressor of the present invention can obtain a stable high refrigeration capacity by constantly increasing the suction pressure regardless of changes in operating conditions.

The hermetic compressor according to claim 9 of the present invention comprises:
The hermetic compressor according to any one of claims 1 to 3, wherein the suction passage has a bent portion, and the bent portion has a substantially uniform curvature.

Accordingly, the hermetic compressor of the present invention can reduce the attenuation of the pressure amplitude of the pressure wave or the reflected wave, increase the suction pressure, and improve the high refrigerating capacity.

The hermetic compressor according to claim 10 of the present invention is:
The suction flow path is bent a plurality of times, and the suction flow paths are formed to be close to each other.

Accordingly, the hermetic compressor of the present invention reduces the amount of heat received in the suction passage from the high-temperature refrigerant gas in the closed vessel, reduces the temperature rise in the suction passage, and reduces the suction gas in the suction passage. A rise in temperature is suppressed, and a large refrigerant circulation amount is obtained.

At the same time, the hermetic compressor of the present invention has a low suction gas temperature and sucks a high-density refrigerant gas into the suction flow path, so that the sound speed of the suction gas is reduced. The influence is increased, a large pressure wave is generated, and a high refrigeration capacity can be obtained.

The hermetic compressor according to claim 11 of the present invention comprises:
A resonance type muffler is formed in the suction passage.

Accordingly, the hermetic compressor of the present invention can attenuate the noise generated due to the pulsation of the refrigerant gas to be sucked by the resonance type muffler provided in the suction passage without reducing the refrigeration capacity. Therefore, the noise transmitted to the inside of the closed container can be reduced, and the noise finally transmitted to the outside of the closed container can be reduced.

The hermetic compressor according to claim 12 of the present invention comprises:
A suction lead for opening and closing the suction hole, wherein an axial direction of the suction flow path at a directly connected portion between the suction hole and the suction flow path has an angle smaller than 90 degrees with respect to a connection surface of the valve plate. It is comprised in.

Thus, the hermetic compressor of the present invention has a structure in which, when the reflected wave returns to the inside of the cylinder, the reflected wave is easily reflected directly into the cylinder without being reflected by the suction lead, and the reflected wave is reflected by the suction lead. In this case, since the angle between the direction in which the reflected wave travels and the suction lead is small, the direction in which the reflected wave travels after reflection is not significantly changed, and the reflected wave easily enters the cylinder. That is, the reflected wave is less likely to be disturbed by the suction reed, and the pressure energy of the reflected wave is effectively entered into the cylinder, and the hermetic compressor of the present invention has a large refrigeration capacity.

The hermetic compressor according to claim 13 of the present invention comprises:
A suction lead for opening and closing the suction hole,
A deflection control mechanism for controlling an initial deflection amount of the suction lead.

As a result, the hermetic compressor of the present invention is configured such that a large refrigeration capacity is not obtained at a low outside air temperature that does not require a large refrigeration capacity, suppresses power consumption, and requires a large refrigeration capacity. When the outside air temperature is high, a large refrigeration capacity as before can be obtained, and the total power consumption can be reduced by controlling the refrigeration capacity.

Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(Embodiment 1)
First, Embodiment 1 which is an example of the hermetic-type compressor of the present invention will be described.

FIG. 1 is a cross-sectional plan view of a hermetic compressor shown to explain a general compressor configuration among the hermetic compressor configurations according to the first embodiment of the present invention. FIG. 2 is a vertical cross-sectional view of the hermetic compressor shown to explain the configuration of a general compressor among the hermetic compressors according to the first embodiment. FIG. 3 is a plan sectional view of the hermetic compressor according to Embodiment 1 of the present invention. FIG. 4 is a schematic block diagram of a hermetic compressor and a control block diagram of a refrigeration apparatus according to the first embodiment. FIG. 5 is a characteristic diagram showing a change in refrigeration capacity at the time of controlling the rotation speed of the hermetic-type compressor of the first embodiment using the inverter device.

1 and 2, the hermetic compressor 1 has a hermetic container 2 composed of a lower shell 3 and an upper shell 4. The electric compression element 81 in the closed container 2 is elastically supported by the closed container 2 by the coil spring 8 so that the compression element 300 is disposed in the upper part and the electric motor 211 is disposed in the lower part. The compression element 300 includes a cylinder 10 provided integrally with the block 9, a piston 11 reciprocating left and right in FIG. 1 on an arrow w in FIG. 1, a crankshaft 12, a connecting rod 13 (connecting rod), and the like. I have. The electric motor 211 is configured by a rotor, a stator, and the like, which are fixed to the crankshaft 12 by shrink fitting (fitting and fixing after heating). The stator is fixed to the block 9 with screws. The lubricating oil 17 is stored in the lower part of the closed container 2.

One end of a suction pipe 193 serving as a suction passage for sucking the refrigerant gas into the cylinder 10 is attached to the compression element 300 via the suction chamber 25, and the other end is disposed in the closed container 2 as an open end 193a. ing. For this reason, the suction pipe 193 connects the inside of the cylinder 10 and the inside of the closed container 2.

Next, a specific configuration of the hermetic compressor according to the first embodiment of the present invention will be described.

3 and 4, the suction pipe 193 is a suction pipe serving as a suction flow path having one end open to the space inside the closed casing 2 and the other end almost directly connected to the suction hole 150 a of the valve plate 150. The inverter device 212 shown in FIG. 4 operates the electric motor 211 at at least two or more specific frequencies.

Next, the operation of the hermetic compressor of the first embodiment configured as described above will be described.

Generally, at low outside temperatures, freezing and refrigeration equipment does not require large refrigeration capacity. However, in such a situation, if the conventional hermetic compressor supplies more refrigerant than necessary, the suction pressure decreases and the discharge pressure increases. As a result, there is a problem that the efficiency of the entire refrigeration system including the conventional hermetic compressor is reduced, and as a result, the total power consumption is increased.

を In order to solve this problem, the power consumption can be reduced by reducing the refrigerant circulation amount at low outside temperatures.

In the hermetic compressor of the first embodiment, the pressure wave generated near the suction hole 150a during the suction stroke propagates in the direction opposite to the flow of the refrigerant gas. Then, the pressure wave becomes a reflected wave whose phase is inverted in the space inside the closed container 2, propagates in the forward direction with the flow of the refrigerant gas, and returns to the suction hole 150a.

(4) By causing the reflected wave to reach the suction hole 150a during the suction stroke, the pressure energy of the reflected wave is added to the refrigerant gas at the time of completion of suction, and the suction pressure of the refrigerant gas increases.

Therefore, in the hermetic compressor of the first embodiment, the cylinder 10 is filled with a refrigerant gas having a higher density. Therefore, in the hermetic compressor of the first embodiment, the amount of refrigerant discharged per compression stroke increases, and the amount of circulating refrigerant increases. Due to such a supercharging effect, the hermetic compressor of the first embodiment can greatly improve the refrigeration capacity.

Next, a specific example of the supercharging effect will be described with reference to FIG. FIG. 5 is a characteristic diagram showing a change in refrigeration capacity when the number of revolutions of the hermetic compressor is controlled using the inverter device. In FIG. 5, the horizontal axis represents the rotation speed (r / s), and the vertical axis represents the refrigerating capacity relative value. The relative refrigeration value is based on the case where the rotation speed of the conventional hermetic compressor is 60 Hz. In FIG. 5, the solid line shows the case where the rotation speed of the conventional hermetic compressor is controlled. Dashed lines (1) and (2) show the cases where the hermetic compressors having different cylinder capacities in the first embodiment are controlled in rotation speed. In FIG. 5, the dashed line indicates the case where the refrigerating capacity increases in proportion to the rotation speed.

When a conventional reciprocating hermetic compressor for controlling the rotation speed is used to obtain a supercharging effect at the time of operation at a frequency of 60 Hz, the refrigerating capacity changes as shown by a broken line (1) in FIG. I do.

As shown by the solid line in FIG. 5, in the conventional hermetic compressor, when the rotational speed is higher than 50 Hz, the refrigerating capacity proportional to the increase in the rotational speed cannot be obtained due to problems such as the followability of the valve mechanism. , The refrigeration capacity is saturated and further reduced.

However, according to the hermetic-type compressor of the first embodiment, the refrigerating capacity is significantly improved in the vicinity of the high-speed side rotation speed of 60 Hz due to the supercharging as compared with the conventional apparatus. A considerable increase in abilities was seen. As shown by the broken line (1) in FIG. 5, the hermetic compressor of the first embodiment has a refrigerating capacity equivalent to that at 70 Hz operation on the assumption that the refrigerating capacity is obtained in proportion to an increase in the rotation speed. I was able to secure it.

(5) As shown in FIG. 5, the same refrigerating capacity as that of the conventional apparatus at the time of 60 Hz operation was obtained by the hermetic compressor of the first embodiment having a cylinder capacity approximately 20% smaller as indicated by a broken line (2).

As described above, according to the hermetic-type compressor of Embodiment 1, the range of the refrigerating capacity can be widened, and the refrigerating capacity according to the outside air temperature and the load can be obtained. Further, as shown by the broken line (2) in FIG. 5, the closed type compressor having a smaller cylinder capacity than the conventional type can be configured so as to obtain a refrigerating capacity substantially equal to that of the conventional type. Can be achieved.

Thereby, according to the hermetic-type compressor of the first embodiment, by performing supercharging in addition to controlling the rotation speed, a refrigerating capacity according to the outside air temperature and the load can be obtained, and the power consumption can be reduced. .

As described above, the hermetic compressor according to the first embodiment includes the hermetic container 2, the electric compression element 81 housed in the hermetic container 2, and configured by the compression element 300 and the electric motor 211, and the compression element 300. Operating the electric motor 211, the cylinder 10, the valve plate 150 having the suction hole 150a, the suction pipe 193 having one end opened in the closed container 1 or a space such as an accumulator and the other end being substantially directly connected to the suction hole 150a. And an inverter 212. For this reason, the hermetic-type compressor of Embodiment 1 can obtain the refrigerating capacity according to the outside air temperature and the load, and can reduce the power consumption.

密閉 Needless to say, the hermetic-type compressor of the first embodiment can obtain the same effects as those of the first embodiment even with a rotary-type or scroll-type compressor.

In the first embodiment, the suction pipe is used as the suction flow channel. However, the same effect as in the first embodiment can be obtained by using a block having a suction flow path.

(Embodiment 2)
Next, a second embodiment which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 6 is a longitudinal sectional view showing a hermetic compressor according to Embodiment 2 of the present invention. FIG. 7 is a front sectional view of the hermetic compressor of FIG. 6 taken along line EE.

In the hermetic-type compressor of the second embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof will be omitted.

6 and 7, a suction hole 193a is formed in the valve plate 193 fixed to the end face of the cylinder 10 of the compression element 6, and the suction hole 193a is formed in the first suction pipe 231 (suction flow path). Directly connected to one end. The other end of the first suction pipe 231 is disposed at a predetermined position in the space inside the sealed container 2 as an open end 231a. As shown in FIG. 7, the first suction pipe 231 (suction flow path) is bent a plurality of times so that the suction flow paths are close to each other.

吸入 As shown in FIG. 7, the hermetic compressor according to the second embodiment is provided with a suction muffler 241. The suction muffler 241 is configured to substantially surround the first suction pipe 231. The suction muffler 241 has a volume necessary to reflect the pressure wave.

Next, the operation of the hermetic compressor of the second embodiment configured as described above will be described.

The pressure wave generated in the vicinity of the suction hole 193a of the valve plate 193 during the suction stroke propagates in the direction opposite to the flow of the refrigerant gas, becomes a reflected wave whose phase is inverted in the space inside the closed container 2, and is sequentially reflected by the flow of the refrigerant gas. And returns to the suction hole 193a.

(4) During the suction stroke, the reflected wave reaches the suction hole 193a, so that the pressure energy of the reflected wave at the time when suction is completed is added to the refrigerant gas, and the suction pressure of the refrigerant gas increases.

Therefore, in the hermetic compressor according to the seventeenth embodiment, the cylinder 10 is filled with a refrigerant gas having a higher density. For this reason, the hermetic-type compressor of Embodiment 2 can increase the amount of refrigerant discharged per compression stroke, increase the amount of circulating refrigerant, and improve refrigeration capacity.

At this time, in the hermetic-type compressor of the second embodiment, the open end 231a of the first suction pipe 231 is disposed in the suction muffler 241. For this reason, in the hermetic compressor of the second embodiment, the pulsation of the suction gas is attenuated by the suction muffler 241 and the force for exciting the refrigerant gas in the closed container 2 is reduced, and the refrigerant gas in the closed container 2 is reduced. Irrespective of the resonance frequency, the resonance sound can always be reduced.

In the hermetic compressor of the second embodiment, even if the refrigerant gas in the hermetic container 2 resonates, the open end 231a of the first suction pipe 231 is in the suction muffler 241, so that the pressure wave Is reflected by the open end 231a of the suction first suction pipe 231 and is not affected by the resonance of the refrigerant gas in the closed casing 2.

Therefore, when the pressure wave is reflected at the opening end 241a in the suction muffler 241 of the first suction pipe 231 in the hermetic compressor of the second embodiment, the pressure amplitude is affected by the resonance in the space of the hermetic container 2. To prevent attenuation. For this reason, in the hermetic-type compressor of Embodiment 2, the suction pressure of the refrigerant gas always rises, and a stable high refrigeration capacity can be obtained, despite any changes in the shape, operating conditions, and the like of the hermetic container 2. it can.

In the hermetic-type compressor of the second embodiment, by surrounding the first suction pipe 231 with the suction muffler 241, the temperature distribution of the first suction pipe 231 can be made uniform, and the change in sound speed in the refrigerant gas can be reduced. it can. Therefore, the hermetic-type compressor of the second embodiment can reduce the attenuation of the pressure wave, obtain a stable increase in the suction pressure of the refrigerant gas, and obtain a stable improvement effect of the refrigerating capacity. .

In the hermetic compressor according to the second embodiment, the first suction pipe 231 can be made compact, and the hermetic container 2 can be downsized.

As described above, the hermetic compressor according to the second embodiment includes a valve plate 191 having a suction hole 191a and disposed on an end face of a cylinder 10, one end of which opens into the space inside the hermetic container 2, and the other end. Includes a first suction pipe 231 almost directly connected to a suction hole 191 a of the valve plate 191, and a suction muffler 241 substantially wrapping around the first suction pipe 231. For this reason, the hermetic-type compressor of the second embodiment reduces the pulsation of the suction gas to reduce the force for exciting the refrigerant gas in the hermetic container 2, and is independent of the resonance frequency of the refrigerant gas in the hermetic container 2. And the resonance can always be reduced.

The hermetic-type compressor according to the second embodiment always suppresses the attenuation of the pressure amplitude when the pressure wave is reflected at the open end 231 a of the first suction pipe 231 irrespective of the resonance frequency of the refrigerant gas in the hermetic container 2. Can be prevented. The hermetic-type compressor according to the second embodiment can constantly increase the suction pressure of the refrigerant gas and obtain a stable and high refrigeration capacity, regardless of any changes in the shape, operating conditions, and the like of the hermetic container 2.

The hermetic compressor according to the second embodiment can make the temperature distribution of the first suction pipe 231 uniform and reduce the change in sound speed in the refrigerant gas. Therefore, the hermetic-type compressor of the second embodiment can obtain a stable refrigeration capacity by reducing the attenuation of the pressure wave and obtaining a stable increase in the suction pressure.

In the second embodiment, the first suction pipe 231 is substantially directly connected to the suction hole 191a of the valve plate 191. However, even when the first suction pipe 231 and the suction hole 191a of the valve plate 191 are connected via a small space (a flow space having substantially the same cross-sectional shape), substantially the same as in the second embodiment described above. The effect is obtained.

In the second embodiment, the suction channel is described as the tubular first suction pipe 231. However, for example, the same effect as in the second embodiment can be obtained even with a block-shaped one having a suction passage formed therein.

(Embodiment 3)
Next, a third embodiment which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 8 is a longitudinal sectional view of the hermetic compressor according to the third embodiment of the present invention. FIG. 9 is a longitudinal sectional view of the hermetic compressor of the third embodiment. FIG. 10 is an explanatory diagram showing the relationship between the behavior of the refrigerant gas and the crankshaft in the hermetic compressor according to the third embodiment. In the hermetic-type compressor of the third embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof will be omitted.

8 and 9, a suction hole 19a is formed in the valve plate 19 fixed to the end face of the cylinder 10 of the compression element 6, and one end of a suction pipe 229 as a suction passage is formed in the suction hole 19a. Directly connected. The other end of the suction pipe 229 is disposed in the space inside the closed container 2 as an open end 229a.

In FIG. 10, at the start of the suction stroke of the refrigerant gas (at the time point (a) in FIG. 10), the crankshaft 12 is at the reference position, and the suction hole 19a of the valve plate 19 is closed. For this reason, the flow of the refrigerant gas has stopped.

Next, the crankshaft 12 rotates, the piston 11 moves to the right, and the volume in the cylinder 10 increases rapidly. As a result, a pressure difference is generated between the space in the cylinder 10 and the space in the closed container 2, and the suction lead 20 starts to open (at the time point (b) in FIG. 10). The rotational position of the crankshaft 12 at this time (hereinafter, referred to as a crank angle) is defined as θs (rad).

(4) The suction lead 20 is opened, and the refrigerant gas starts flowing to the right (toward the cylinder 10) in the suction pipe 229. At the same time, a pressure wave Wa is generated in the cylinder 10 due to a sudden increase in the volume in the cylinder 10. The pressure wave Wa in the cylinder 10 propagates through the suction pipe 229 through the suction hole 19a, which is an opening, in the direction opposite to the flow of the refrigerant gas toward the space in the closed container 2 in the opposite direction.

(4) The pressure wave Wa that has reached the space inside the closed container 2 becomes a reflected wave Wb that is inverted in the space inside the closed container 2 where the refrigerant gas is stagnant. The reflected wave Wb propagates in the suction pipe 229 in the same direction as the flow of the refrigerant gas (at the time point (c) in FIG. 10).

{Circle around (1)} The reflected wave Wb propagates in the forward direction with the flow of the refrigerant gas and returns to the suction hole 19a of the valve plate 19 (at the time point (d) in FIG. 10).

Assuming that the crank angle at the top dead center shown in FIG. 10A is 0 (rad), the crank angle at which the suction lead 20 starts to open (FIG. 10B) is θs (rad), and the suction pipe 229 is formed. Is set to L (m), the rotation speed of the crankshaft 12 is set to f (Hz), the sound speed in the refrigerant gas sucked in the suction pipe 229 is set to As (m / sec), Assuming that the crank angle at which the pressure wave generated at 19a returns to the suction hole 19a as a reflected wave is θr (rad), these relationships are expressed by the following (Equation 1).

θr = θs + 4π × L × f / As (1)
1.4 (rad) ≦ θr ≦ 3.0 (rad) (2)
At this time, the length L and the like of the suction pipe 229 are adjusted so that the return crank angle θr of the pressure wave falls within the range of (Equation 2).

Next, the operation of the hermetic compressor of the third embodiment configured as described above will be described.

(4) The pressure wave Wa generated simultaneously with the opening of the suction lead 20 during the suction stroke propagates in the direction opposite to the flow of the refrigerant gas. It further becomes a reflected wave Wb whose phase is inverted in the space inside the closed container 2, propagates in the forward direction with the flow of the refrigerant gas, and returns to the suction hole 19a. Further, since the reflected wave Wb has a width, the wave front of the reflected wave returns to the suction hole 19a at the crank angle θr represented by (Equation 1). When the crank angle further advances later, the tail of the reflected wave Wb returns to the suction hole 19a, and the return of the wide reflected wave Wb is completed.

Next, the relationship between the crank angle when the reflected wave Wb returns to the suction hole 19a and the effect of improving the refrigerating capacity will be described by taking the length of the suction pipe 229 as an example.

(4) When the length L of the suction pipe 229 is short, the return crank angle θr of the reflected wave Wb becomes small, as can be seen from (Equation 1), that is, the reflected wave Wb returns at an early timing of the suction stroke. Therefore, before the suction stroke is completed, all of the reflected waves Wb having a width may return to the suction hole 19a and end. In this case, after the return of the reflected wave Wb is completed, the pressure in the suction hole 19a decreases, and even though the suction stroke is in progress, the suction lead 20 is closed or the suction pipe is moved from inside the cylinder 10. For example, the refrigerant gas may flow backward to 229. For this reason, the density of the refrigerant gas sucked into the cylinder 10 cannot be sufficiently increased, and the effect of improving the refrigerating capacity is reduced.

逆 Conversely, when the length L of the suction pipe 229 is long, the reflected wave Wb returns at a timing late in the suction stroke. Or it will come back after the suction stroke is over. Therefore, the suction stroke ends before all the reflected waves Wb having a width return to the suction holes 19a, and the density of the refrigerant gas sucked into the cylinder 10 cannot be sufficiently increased. Therefore, the effect of improving the refrigerating capacity is reduced.

Thus, if the length of the suction pipe 229 is too short or too long, the effect of improving the refrigerating capacity will be small. There is an optimum length of the suction pipe 229 at which the effect of improving the refrigerating capacity is maximized, that is, an optimum return crank angle θr of the reflected wave Wb. However, since the reflected wave Wb has a width, the return crank angle of the reflected wave at which the effect of improving the refrigerating capacity is almost maximized also has a width. In the case of the reciprocating hermetic compressor, the effect of improving the refrigerating capacity can be obtained to the maximum extent in the range of (Expression 2) for the return crank angle θr of the reflected wave.

For example, when the refrigerant is HFC-134a, the pressure of the refrigerant gas to be sucked is 0.085 (MPa), and the temperature of the refrigerant gas is 80 (° C.), the sound speed As is 176.3 (m / s). . Assuming that the rotational speed f of the crack shaft 12 is 58.5 (Hz) and the crank angle θs at which the suction lead 20 starts to be opened is 0.96 (rad), the suction pipe 229 is required to satisfy (Equation 2). May be set to 0.10 to 0.48 (m).

As described above, in the hermetic-type compressor according to the third embodiment of the present invention, the length of the suction pipe 229 and the like are adjusted so that the return crank angle of the reflected wave is optimized. Is obtained.

As described above, in the hermetic compressor of the third embodiment, the crank angle at which the suction lead 20 starts to open is θs (rad), the length of the suction pipe 229 is L (m), Assuming that the number of revolutions is f (Hz) and the speed of sound in the refrigerant gas sucked in the suction pipe 229 is As (m / sec), the pressure wave generated in the suction hole 19a at the start of suction and represented by (Equation 1) The return crank angle θr (rad) is configured to be in the range of (Equation 2).

Therefore, in the hermetic-type compressor according to the third embodiment, the crank angle at which the reflected wave Wb returns to the suction hole 19a is optimized, and the suction pressure is increased to obtain the maximum effect of improving the refrigerating capacity. .

In the case where the refrigerant type and the pressure and temperature of the refrigerant gas to be sucked are different and the sound speed is different, if the length of the suction pipe 229 is adjusted so that the return crank angle of the reflected wave Wb satisfies (Equation 2), The same effect as in the third embodiment can be obtained. Even if the rotation frequency of the crankshaft 12 and the crank angle at which the suction lead 20 starts to open are different, if the length of the suction pipe 229 is adjusted so that the return crank angle of the reflected wave Wb satisfies (Equation 2). Thus, the same effect as in the third embodiment can be obtained.

(Embodiment 4)
Next, a fourth embodiment which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 11 is a longitudinal sectional view of a hermetic compressor according to Embodiment 4 of the present invention. FIG. 12 is a plan sectional view of a hermetic compressor according to Embodiment 4 of the present invention. In the hermetic-type compressor of the fourth embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof will be omitted.

11 and 12, a suction hole 19a is formed in a valve plate 19 fixed to the end face of the cylinder 10 of the compression element 6, and one end of a suction pipe 23 is directly connected to the suction hole 19a. . The other end of the suction pipe 23 is arranged in the space inside the closed container 2 as an open end 23a.

In FIGS. 11 and 12, the closed container 2 is composed of a lower shell 3 and an upper shell 4. In FIG. 12, reference symbol a is the maximum distance in the direction perpendicular to the reciprocating direction of the piston 11 on the inner surface of the closed container 2, and reference symbol b is the maximum distance in the reciprocating direction of the piston 11 on the inner surface of the closed container 2. Reference symbol c in FIG. 11 is the maximum distance in the axial direction of the crankshaft 12 from the inner surface of the closed casing 2 to the surface of the lubricating oil 17. Corresponding to the respective lengths of a, b, and c, the refrigerant gas in the sealed container 2 has a unique resonance frequency in each direction. In the hermetic compressor according to the fourth embodiment, the distances a, b, c, and the like are adjusted so that their resonance frequencies do not become near an integral multiple of the number of revolutions of the crankshaft 12.

Next, the operation of the hermetic compressor of the fourth embodiment configured as described above will be described.

The pressure wave generated at the same time as the suction lead 20 is opened during the suction stroke propagates in the direction opposite to the flow of the refrigerant gas, becomes a reflection plate whose phase is inverted in the space inside the closed container 2, and moves in the forward direction with the flow of the refrigerant gas. It propagates and returns to the suction hole 19a.

If the refrigerant gas in the closed vessel 2 resonates, not only will the noise increase, but also if the pressure wave is reflected at the open end 23a of the suction pipe 23, the refrigerant gas in the closed vessel 2 will resonate, that is, stand still. Under the influence of waves, losses occur. Therefore, the pressure amplitude of the reflected wave is reduced, the rate of increase of the suction pressure is reduced, and the effect of improving the refrigerating capacity is reduced.

(4) The refrigerant gas in the closed vessel 2 resonates when the resonance frequency in the closed vessel 2 and the operating frequency of the closed type compressor are substantially equal to each other, that is, when the vibration frequency is substantially the same.

Generally, regarding the resonance generated between the opposing walls, the following formula (Equation 3) exists between the distance Lw between the two walls, the resonance frequency fr, and the sound velocity Ac of the medium.

Lw = Ac / (2fr) (Equation 3)
Applying the relationship of (Equation 3) to a hermetic compressor, Lw is the distance between the inner surfaces of the facing hermetic containers 2, fr is the resonance frequency that can be generated between the inner surfaces of the hermetic containers 2 facing each other, and Ac is Is the sound speed of the refrigerant. That is, if the lengths a, b, and c in the respective directions of the inner surface of the closed container 2 are determined so that the resonance frequency of the closed container 2 does not approach an integral multiple of the operation frequency, no resonance occurs. However, in reality, Lw calculated by (Equation 3) slightly deviates due to the influence of the compression element 6, the electric motor 7, etc. in the closed vessel 2, so that it is necessary to apply a correction coefficient obtained from comparison with the result of an acoustic experiment or a numerical analysis. There is a sound experiment and a numerical analysis performed by the inventor, and it is known that the correction value is 0.977. Therefore, resonance does not occur if the lengths a, b, and c in the respective directions are determined in consideration of the correction value. As described above, in the hermetic compressor according to the fourth embodiment, since the refrigerant gas in the hermetic container 2 does not resonate, the generation of resonance noise is prevented, and the pressure when the pressure wave is reflected at the open end 23 a of the suction pipe 23 is reduced. The amplitude is prevented from attenuating, the suction pressure is constantly increased, and the effect of improving the refrigerating capacity is obtained.

As described above, the hermetic-type compressor of the fourth embodiment is configured such that the resonance frequency of the refrigerant gas in the hermetic container 2 does not become near an integral multiple of the rotation speed of the crankshaft 12. The refrigerant gas inside does not resonate. For this reason, the hermetic-type compressor of the fourth embodiment prevents the generation of resonance noise and the attenuation of the pressure amplitude when the pressure wave is reflected at the open end 23a of the suction pipe 23, so that the suction pressure always increases. Thus, the effect of improving the refrigerating capacity is obtained.

(Embodiment 5)
Next, a fifth embodiment which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 13 is a longitudinal sectional view of a hermetic compressor according to Embodiment 5 of the present invention. FIG. 14 is a plan sectional view of the hermetic compressor of FIG. 13 taken along line BB. In the hermetic-type compressor of the fifth embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof will be omitted.

13 and 14, a suction hole 19a is formed in a valve plate 19 fixed to the end face of the cylinder 10 of the compression element 6, and one end of a suction pipe 200 as a suction passage is formed in the suction hole 19a. Directly connected. The other end of the suction pipe 200 is arranged in the space inside the sealed container 2 as an open end 200a.

At least a part of the suction pipe 200 is formed of a material having low thermal conductivity such as Teflon (registered trademark) or PBT.

Next, the operation of the hermetic compressor of the fifth embodiment configured as described above will be described.

The pressure wave generated in the cylinder 10 passes through the suction hole 19a of the valve plate 19, propagates in the direction opposite to the flow of the refrigerant gas, and becomes a reflected wave whose phase is inverted in the space inside the closed container 2. This reflected wave propagates in the forward direction with the flow of the refrigerant gas and returns to the suction hole 16a.

(4) During the suction stroke, the reflected wave reaches the suction hole 19a, so that the pressure energy of the reflected wave is added when the suction is completed, and the suction pressure of the refrigerant gas increases.

Therefore, the cylinder 10 is filled with a refrigerant gas having a higher density, and the amount of refrigerant discharged per compression stroke increases. As a result, in the hermetic-type compressor of the fifth embodiment, the amount of circulating refrigerant is increased, and the refrigeration capacity is significantly improved.

In the hermetic-type compressor according to the fifth embodiment, at least a part of the suction pipe 200 is formed of a material having low thermal conductivity such as Teflon (registered trademark) or PBT, so that time elapses after the start of the hermetic-type compressor. Accordingly, even if the temperature of the cylinder head 80 and the like greatly rises, heat can be prevented from being transmitted to the suction pipe 200, and the temperature change of the suction pipe 200 can be reduced. For this reason, the hermetic-type compressor of the fifth embodiment can reduce the change in the speed of sound in the refrigerant gas in the suction pipe 200. For this reason, the hermetic-type compressor of Embodiment 5 can generate a stable pressure wave and obtain a high increasing effect of the suction pressure, and can achieve a stable high refrigeration capacity without being affected by the lapse of time after startup. Obtainable.

The hermetic compressor according to the fifth embodiment can supply a low-temperature refrigerant gas into the cylinder 10, and can improve the refrigerant circulation amount.

As described above, in the hermetic-type compressor of the fifth embodiment, one end of the suction pipe 200 opens into the space inside the hermetic container 2, the other end is directly connected to the suction hole 19a of the valve plate 19, and The portion is formed of a material having low thermal conductivity such as Teflon (registered trademark) or PBT.

Therefore, even if the temperature of the cylinder head 80 and the like greatly rises with the lapse of time after the start of the hermetic compressor, heat is prevented from conducting through the suction pipe 200, and the temperature change of the suction pipe 200 is reduced. . Thus, the change in the speed of sound in the refrigerant gas in the suction pipe 200 can be reduced.

As a result, the hermetic-type compressor of the fifth embodiment can generate a stable pressure wave and increase the suction pressure, and can obtain a stable and high refrigeration capacity without being affected by the elapse of time after startup. it can.

The hermetic compressor according to the fifth embodiment can supply a low-temperature refrigerant gas into the cylinder 10, and can improve the refrigerant circulation amount.

In the fifth embodiment, a hermetic compressor using a suction pipe formed of a material having low thermal conductivity has been described. However, the same effect as in the fifth embodiment can be obtained by using a material having a low thermal conductivity only partially near the cylinder portion.

(Embodiment 6)
Next, a sixth embodiment which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 15 is a longitudinal sectional view of a hermetic compressor according to Embodiment 6 of the present invention. FIG. 16 is a plan sectional view of the hermetic compressor of FIG. 15 taken along line CC. FIG. 17 is a characteristic diagram showing a change in the suction pressure increase ratio. FIG. 18 is a characteristic diagram showing a change in the refrigeration capacity improvement ratio. FIG. 19 is a characteristic diagram showing a change in the noise change rate. In the hermetic-type compressor of the sixth embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof will be omitted.

15 and 16, a suction hole 19a is formed in a valve plate 19 fixed to the end face of the cylinder 10 of the compression element 6, and a first suction pipe 210 as a suction flow passage is formed in the suction hole 19a. Are directly connected. The other end of the first suction pipe 210 is arranged in the space inside the closed container 2 as an open end 210a, and is arranged near the open end 190a of the second suction pipe 190.

Next, the operation of the hermetic compressor according to the sixth embodiment configured as described above will be described.

The pressure wave generated in the cylinder 10 passes through the suction hole 19 a of the valve plate 19, propagates in the direction opposite to the flow of the refrigerant gas, and becomes a reflected wave whose phase is inverted in the space inside the closed container 2. This reflected wave propagates in the forward direction with the flow of the refrigerant gas and returns to the suction hole 19a.

(4) During the suction stroke, when the reflected wave reaches the suction hole 19a, the pressure energy of the reflected wave is added to the refrigerant gas at the time of completion of the suction, and the suction pressure of the refrigerant gas increases.

Therefore, the cylinder 10 is filled with a refrigerant gas having a higher density, the amount of refrigerant discharged per compression stroke increases, and the refrigerant circulation amount increases. As a result, the hermetic compressor of the tenth embodiment has a significantly improved refrigerating capacity.

In the hermetic compressor of the sixth embodiment, the open end 210a of the first suction pipe 210 is disposed near the open end 190a of the second suction pipe 190 in the closed casing 2. Therefore, the hermetic-type compressor according to the sixth embodiment can suck the refrigerant gas having a low temperature and a high density into the first suction pipe 210, and the speed of sound in the refrigerant gas is reduced. For this reason, the hermetic-type compressor of Embodiment 6 has a large influence on the compressibility, and can generate a large pressure wave.

Thereby, the hermetic-type compressor of Embodiment 6 can increase the suction pressure increasing effect. The hermetic-type compressor according to the sixth embodiment allows the refrigerant gas having a low temperature to be sucked into the cylinder 10, thereby greatly increasing the effect of improving the refrigerating capacity, and obtaining a high refrigerating capacity with high efficiency. .

In the hermetic compressor according to the sixth embodiment, pressure pulsation from second suction pipe 190 is caused by the gap between open end 190a of second suction pipe 190 and open end 210a of first suction pipe 210. Transmission to the refrigeration cycle is reduced. For this reason, the hermetic compressor of the sixth embodiment can significantly reduce noise.

The distance between the open end 210a of the first suction pipe 210 and the open end 190a of the second suction pipe 190 (distance between the open ends) increases the effect of increasing the suction pressure and improves the refrigerating capacity. According to experiments performed by the inventor, it has been found that a distance between 3 mm and 50 mm is preferable in order to increase the noise reduction effect and the noise reduction effect.

The results are shown in FIGS. 17, 18 and 19. In FIG. 17, the vertical axis shows the suction pressure increase ratio (%), and the horizontal axis shows the opening between the open end 190a of the second suction pipe 190 and the open end 210a of the first suction pipe 210. It is the graph which showed the distance (mm) between edge parts. The suction pressure increase ratio in FIG. 17 indicates the ratio of the pressure of the reflected wave reflected by the pressure wave in the space in the closed container 2 to the pressure of the pressure wave generated in the cylinder 10.

FIG. 18 is a graph showing the refrigeration capacity improvement ratio (%) on the vertical axis and the distance between the open ends (mm) on the horizontal axis. The refrigeration capacity improvement ratio in FIG. 18 is a ratio of the measured refrigeration capacity to the maximum refrigeration capacity.

FIG. 19 shows the noise change rate (%) on the vertical axis and the distance between opening ends (mm) on the horizontal axis. The noise change rate in FIG. 19 indicates a change in noise pressure when the distance between openings is 0 mm and 100%.

As described above, in the hermetic-type compressor of the sixth embodiment, one end of the first suction pipe 210 is directly connected to the suction hole 19a of the valve plate 19, and the other end is the second suction pipe in the closed container 2. The pipe 190 is disposed near the open end 190a. Therefore, the hermetic-type compressor according to the sixth embodiment can suck the refrigerant gas having a low temperature and a high density into the first suction pipe 210, so that the speed of sound in the refrigerant gas can be reduced. . For this reason, the hermetic-type compressor of Embodiment 6 has a large influence on the compressibility, and can generate a large pressure wave. For this reason, the hermetic-type compressor of the sixth embodiment increases the effect of increasing the suction pressure and also increases the effect of improving the refrigerating capacity by sucking the low-temperature refrigerant gas into the cylinder 10. High refrigeration capacity can be obtained.

In the hermetic-type compressor of the sixth embodiment, the pressure pulsation is reduced by forming a gap between the open end 190a of the second suction pipe 190 and the open end 210a of the first suction pipe 210. Transmission from the suction pipe 190 to the refrigeration cycle can be reduced. Therefore, the hermetic-type compressor of the sixth embodiment can significantly reduce noise.

In addition, the opening end 210a of the first suction pipe 210 serving as the suction passage is widened so as to face the opening end 190a of the second suction pipe 190, so that the refrigerant gas can easily flow, and the refrigeration capacity can be improved. It is needless to say that the improvement can be achieved.

(Embodiment 7)
Next, a seventh embodiment which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 20 is a longitudinal sectional view of a hermetic compressor according to Embodiment 7 of the present invention. FIG. 21 is a plan sectional view taken along line DD of the hermetic compressor of FIG. FIG. 22 is a longitudinal sectional view of the open end of the first suction pipe according to the seventh embodiment. FIG. 23 is a diagram illustrating an opening surface of an opening end of a first suction pipe according to the seventh embodiment.

In the hermetic-type compressor of the seventh embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof is omitted.

20 and 21, a suction hole 19a is formed in a valve plate 19 fixed to an end face of the cylinder 10 of the compression element 6, and a first suction pipe 220 serving as a suction passage is formed in the suction hole 19a. Are directly connected. The other end of the first suction pipe 220 is arranged in the closed container 2 space as an open end 220a. The second suction pipe 190 has an open end 190 a disposed in the internal space of the closed casing 2.

As shown in FIGS. 21 and 22, the first suction pipe 220 has a plurality of open ends 220 a, one end of which is directly connected to the suction hole 19 a of the valve plate 19 and the other end of which is open to the space inside the closed container 2. 220b, and the length from the suction hole 19a to the plurality of opening ends 220a, 220b is different.

Next, the operation of the hermetic compressor according to the seventh embodiment configured as described above will be described.

The pressure wave generated in the cylinder 10 passes through the suction hole 19 a of the valve plate 19, propagates in the direction opposite to the flow of the refrigerant gas, and becomes a reflected wave whose phase is inverted in the space inside the closed container 2. This reflected wave propagates in the forward direction with the flow of the refrigerant gas and reaches the suction hole 19a.

(4) During the suction stroke, when the reflected wave reaches the suction hole 19a, the pressure energy of the reflected wave is added to the refrigerant gas when the suction is completed, and the suction pressure increases.

Therefore, the cylinder 10 is filled with a refrigerant gas having a higher density, the amount of refrigerant discharged per compression stroke increases, and the refrigerant circulation amount increases. As a result, according to the hermetic compressor of the seventh embodiment, the refrigerating capacity can be significantly improved.

At this time, the pressure wave generated in the suction hole 19a is reflected one after another by the plurality of opening ends 220a and 220b having different lengths from the suction hole 19a to the opening end, reaches the suction hole 19a, and enters the cylinder 10. Supplied.

Accordingly, the hermetic compressor of the seventh embodiment can increase the timing at which the reflected wave reaches the suction port 19a.

Therefore, in the hermetic-type compressor of the seventh embodiment, even if the sound speed in the refrigerant gas changes due to a change in operating conditions or the like, and the timing at which one reflected wave arrives is shifted, other reflected waves are successively generated. It reaches the suction hole 19a. For this reason, the hermetic-type compressor of Embodiment 7 can always supply a high-pressure refrigerant gas into the cylinder 10.

Thereby, the hermetic-type compressor of Embodiment 7 can always obtain a stable high refrigerating capacity by increasing the suction pressure irrespective of a change in operating conditions.

As described above, in the hermetic-type compressor of the seventh embodiment, one end of the first suction pipe 220 is directly connected to the suction hole 19a of the valve plate 19, and the other end opens to the space in the closed container 2. And a plurality of opening ends 220a and 220b having different lengths from the suction hole 19a to the opening end. For this reason, the pressure wave generated in the suction hole 19a is successively reflected by the plurality of opening ends 220a and 220b having different lengths from the suction hole 19a to the opening end.

As a result, the hermetic-type compressor according to the seventh embodiment can increase the timing at which the reflected wave returns to the suction hole 19a. Therefore, in the hermetic-type compressor according to the seventh embodiment, even if the sound speed in the refrigerant gas changes due to a change in operating conditions or the like and the timing at which one reflected wave reaches the suction hole 19a is shifted, the other one after another. The reflected wave reaches the suction hole 19a. Therefore, a high-pressure refrigerant gas is always supplied into the cylinder 10. Thus, according to the hermetic-type compressor of the seventh embodiment, a stable high refrigeration capacity can be obtained by constantly increasing the suction pressure regardless of a change in operating conditions.

In the seventh embodiment, the suction pipe 220 having the plurality of opening ends 220a and 220b having different lengths is used as the suction flow path. The same effect as that of No. 7 can be obtained.

(Embodiment 8)
Next, Embodiment 8 which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 24 is a longitudinal sectional view showing a hermetic compressor according to Embodiment 8 of the present invention. FIG. 25 is a front cross-sectional view of the hermetic compressor of FIG. 24 taken along line BB. FIG. 26 is a longitudinal sectional view showing a hermetic-type compressor having another suction channel shape according to the eighth embodiment. FIG. 27 is a front sectional view of the hermetic compressor of FIG. 26 taken along line CC.

In the hermetic-type compressor of the eighth embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof will be omitted.

24 and 25, a suction hole 191a is formed in a valve plate 191 fixed to the end face of the cylinder 10 of the compression element 6, and the suction hole 191a is directly connected to one end of a suction pipe 201 (suction flow path). It is connected. The other end of the suction pipe 201 is arranged at a predetermined position in the space inside the sealed container 2 as an open end 201a. The suction pipe 201 (suction flow path) has a bent portion 201b having a substantially uniform curvature.

Next, the operation of the hermetic compressor according to the eighth embodiment configured as described above will be described.

The pressure wave generated in the vicinity of the suction hole 191a of the valve plate 191 during the suction stroke propagates in the direction opposite to the flow of the refrigerant gas, becomes a reflected wave whose phase is inverted in the space inside the closed container 2, and is sequentially reflected by the flow of the refrigerant gas. And returns to the suction hole 191a.

(4) During the suction stroke, the reflected wave reaches the suction hole 191a, so that the pressure energy of the reflected wave at the time of completion of suction is added to the refrigerant gas, and the suction pressure of the refrigerant gas increases.

Therefore, in the hermetic-type compressor according to the eighth embodiment, the cylinder 10 is filled with a refrigerant gas having a higher density, and the amount of refrigerant discharged per compression stroke increases, and the amount of circulated refrigerant increases. As a result, the refrigeration capacity can be improved.

Further, the hermetic-type compressor according to the eighth embodiment suppresses a decrease in the amplitude of the pressure wave in the bent portion 201b by making the curvature of each bent portion 201b of the suction pipe 201 substantially uniform, and the reflected wave having a high pressure. Can be returned into the cylinder 10, and higher refrigeration capacity can be improved.

In the hermetic compressor of the eighth embodiment, the suction pipe 201 can be formed compact, and the hermetic container 2 can be downsized.

As described above, the hermetic-type compressor according to the eighth embodiment includes the valve plate 191 having the suction hole 191a and disposed on the end surface of the cylinder 10, one end opening to the space inside the closed container 2, and the other end. And a suction pipe 201 substantially directly connected to the suction hole 191a of the valve plate 191 and having a bent portion 201b having a substantially uniform curvature. For this reason, the hermetic-type compressor of Embodiment 8 can reduce the attenuation of the pressure amplitude of the pressure wave or the reflected wave. Therefore, the hermetic-type compressor of the eighth embodiment can increase the suction pressure and obtain a high refrigeration capacity.

In the hermetic compressor of the eighth embodiment, the curvature of the bent portion 212b is increased by forming the suction pipe, which is the suction flow path, in a spiral suction pipe 212 as shown in FIGS. 26 and 27. be able to. Therefore, the hermetic compressor of the eighth embodiment can further reduce the attenuation of the pressure in suction pipe 212.

In the eighth embodiment, the suction pipes 201 and 212 are substantially directly connected to the suction holes 191a of the valve plate 191. However, even if the suction pipes 201 and 212 and the suction hole 191a of the valve plate 191 are connected via a flow path space having substantially the same cross-sectional area, the same effect as in the eighth embodiment can be obtained.

In the hermetic compressor according to the eighth embodiment, the suction passages are formed by the tubular suction pipes 201 and 212. However, the same effect as in the eighth embodiment can be obtained even if the suction flow path is constituted by, for example, a block having a suction flow path instead of the suction pipe.

(Embodiment 9)
Next, a ninth embodiment which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 28 is a longitudinal sectional view showing a hermetic compressor according to Embodiment 9 of the present invention. FIG. 29 is a front sectional view taken along line DD of the hermetic compressor of FIG.

In the hermetic-type compressor of the ninth embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof will be omitted.

28 and 29, a suction hole 192a is formed in a valve plate 192 fixed to the end face of the cylinder 10 of the compression element 6, and this suction hole 192a is directly connected to one end of a suction pipe 221 (suction flow path). It is connected. The other end of the suction pipe 221 is disposed at a predetermined position in the space inside the closed container 2 as an open end 221a. As shown in FIG. 29, the suction pipe 221 (suction flow path) is bent a plurality of times so that the suction flow paths are close to each other.

Next, the operation of the hermetic compressor of the ninth embodiment configured as described above will be described.

The pressure wave generated in the vicinity of the suction hole 192a of the valve plate 192 during the suction stroke propagates in a direction opposite to the flow of the refrigerant gas, becomes a reflected wave whose phase is inverted in the space inside the closed container 2, and is sequentially reflected by the flow of the refrigerant gas. And returns to the suction hole 192a.

(4) During the suction stroke, the reflected wave reaches the suction hole 192a, so that the pressure energy of the reflected wave at the time of completion of suction is added to the refrigerant gas, and the suction pressure of the refrigerant gas increases.

Therefore, in the hermetic-type compressor according to the eighth embodiment, the cylinder 10 is filled with a refrigerant gas having a higher density, and the amount of refrigerant discharged per compression stroke increases, and the amount of circulated refrigerant increases. As a result, the refrigeration capacity can be improved.

In the hermetic compressor according to the ninth embodiment, the suction pipe 221 is bent a plurality of times, and the suction pipe 221 through which the low-temperature suction gas flows is arranged close to the suction pipe 221. Therefore, the hermetic-type compressor according to the ninth embodiment reduces the influence of the refrigerant gas in the hermetic container 2 that is at a high temperature due to the heat generated by compression in the hermetic container 2, the heat generated by the electric motor, and the heat generated by sliding. be able to.

Thus, in the hermetic-type compressor according to the ninth embodiment, the heat of the high-temperature refrigerant gas in the closed casing 2 is suppressed from being transmitted to the suction pipe 221, and the rise in the temperature of the suction gas in the suction pipe 221 is reduced. be able to. As a result, the hermetic-type compressor of the ninth embodiment can increase the density of the suction gas and increase the amount of circulating refrigerant.

In the hermetic-type compressor of the ninth embodiment, the temperature of the sucked refrigerant gas (the temperature of the suction gas) is low, and the high-density refrigerant gas is sucked into the suction pipe 221. Accordingly, the sound velocity of the suction gas is reduced, so that the effect of compressibility of the refrigerant gas is increased, a large pressure wave is generated, and a high refrigerating capacity can be obtained.

In the hermetic-type compressor of the ninth embodiment, the suction pipe 221 can be formed compact, and the size of the hermetic container can be reduced.

As described above, the hermetic-type compressor according to the ninth embodiment includes a valve plate 191 having a suction hole 191a and disposed on an end surface of a cylinder 10, one end of which opens into the space inside the closed container 2, and the other end. And a suction pipe 221 that is substantially directly connected to the suction hole 191a of the valve plate 191 and that is bent a plurality of times so that the suction flow paths are close to each other. For this reason, the hermetic-type compressor of the ninth embodiment reduces the amount of heat received by the suction pipe 221 from the high-temperature refrigerant gas in the closed casing 1, reduces the temperature rise of the suction pipe 221, and reduces the suction in the suction pipe 221. The rise in gas temperature is reduced. As a result, the hermetic-type compressor of the ninth embodiment can obtain a large refrigerant circulation amount.

と 共 に At the same time, in the hermetic compressor of the ninth embodiment, the suction gas temperature is low, and the high-density refrigerant gas is sucked into the suction pipe 221, so that the sound speed in the sucked refrigerant gas is reduced. For this reason, in the hermetic-type compressor according to the ninth embodiment, the influence of the compressibility of the refrigerant gas is increased, a large pressure wave is generated, and a high refrigerating capacity improvement effect can be obtained.

In the ninth embodiment, the suction pipe 221 is bent a plurality of times to make the suction passages close to each other to reduce the amount of heat received by the suction pipe 221 from the refrigerant gas in the high-temperature closed container. The same effect as that of the hermetic compressor of the ninth embodiment can be obtained even with a block-shaped compressor having a flow path.

In the ninth embodiment, the suction pipes 221 are configured to be close to each other. However, the heat exchange area between the suction pipe 221 and the refrigerant gas in the high-temperature closed container may be reduced by bringing the suction pipes 221 into close contact with each other. With such a configuration, the hermetic-type compressor of the present invention can reduce the amount of heat received by the suction pipe 221 and can further obtain a high refrigerating capacity improving effect.

In the ninth embodiment, the suction pipe 221 is substantially directly connected to the suction hole 191 a of the valve plate 191. However, even if the suction pipe 221 and the suction hole 191a of the valve plate 191 are connected via a passage space having substantially the same cross-sectional area, substantially the same effect can be obtained.

(Embodiment 10)
Next, a tenth embodiment which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 30 is a plan sectional view of a hermetic compressor according to Embodiment 10 of the present invention. FIG. 31 is a front sectional view taken along line BB of FIG. FIG. 32 is a cross-sectional view showing the vicinity of the suction passage of the hermetic compressor according to the tenth embodiment.

In the hermetic compressor of the tenth embodiment, those having the same functions and configurations as those of the hermetic compressors of the above embodiments are denoted by the same reference numerals, and description thereof will be omitted.

30, 31 and 32, one end of a suction flow path 222 formed in the suction block 227 is disposed in the space inside the closed container 2 as an open end, and the other end is substantially in the suction hole 192 a of the valve plate 192. Is directly connected. As shown in FIG. 32, the resonance type muffler 232 formed in the suction block 227 together with the suction flow path 222 has a cavity 242 and a coupling portion 252. The coupling portion 252 of the resonance type muffler 232 has one end opened to the cavity portion 242 and the other end opened to the suction flow passage 222. The volume of the cavity 242 and the coupling portion are adjusted so that the resonance frequency of the resonance type muffler 232 coincides with the frequency of the most problematic noise among the noises generated near the suction hole 192a due to the pulsation of the refrigerant gas to be sucked. The length of the 252, the cross-sectional area of the coupling portion 252, and the like are adjusted.

Next, the operation of the hermetic compressor according to the tenth embodiment configured as described above will be described.

When the refrigerant gas is sucked into the cylinder 10, noise is generated near the suction hole 192a due to the pulsation of the refrigerant gas and the operation of the suction lead. When the generated noise is transmitted through the suction passage 222, the noise is attenuated by the resonance type muffler 232 provided in the suction passage 222. Therefore, the noise transmitted from the suction flow path 222 to the space in the sealed container 2 is reduced, and the noise generated from the sealed compressor can be reduced.

Next, the effect of the resonance type muffler 232 in the tenth embodiment on improving the refrigerating capacity, that is, the effect on the supercharging effect will be described.

周波 数 In the conventional hermetic compressor described in the background art described above, the frequency that is most problematic in noise from the suction passage is usually about 400 Hz to 600 Hz. On the other hand, the frequency of the pressure wave generated during the suction stroke and giving a supercharging effect is considerably small. In addition, the resonance type muffler is generally characterized by a large noise reduction effect only in a narrow frequency band near the resonance frequency.

Therefore, in the tenth embodiment, in the process of returning the pressure wave (expansion wave) generated during the suction stroke to the reflected wave (compression wave) and returning to the suction hole 192a, the resonance type muffler 232 removes only the noise that causes a problem. Since it is attenuated and has little effect on the pressure wave that gives a supercharging effect, a large refrigeration capacity can be obtained in the same manner as without the resonance type muffler 232.

As described above, in the hermetic compressor having the supercharging effect, the configuration in which the resonance type muffler 232 is provided in the suction passage 222 is very effective, and can achieve both the supercharging effect and the noise reduction.

As described above, the hermetic-type compressor according to the tenth embodiment includes the suction flow path 222 having one end opened in the space inside the closed casing 2 and the other end almost directly connected to the suction hole 192a, and the suction flow path 222. And a resonance type muffler 232 provided. For this reason, a large refrigerating capacity can be obtained as before, and the noise generated due to the pulsation of the sucked refrigerant gas is attenuated by the resonance type muffler 232 provided in the suction channel 222, and the noise from the suction channel 222 to the inside of the closed container 2 is reduced. The noise transmitted to the vehicle is reduced.

Therefore, the hermetic compressor according to the tenth embodiment can reduce the noise finally transmitted to the outside of the hermetic container.

In the tenth embodiment, the resonance type muffler 232 is configured to have the cavity portion 242 and the coupling portion 252. However, the resonance type muffler 232 has a configuration in which the cavity portion is directly connected to the suction flow path 222, that is, a so-called side branch type. The same effects as those of the tenth embodiment can be obtained if the resonance type muffler shape is used for other shapes.

(Embodiment 11)
Next, Embodiment 11 which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 33 is a sectional view showing the vicinity of a cylinder of a hermetic compressor according to Embodiment 11 of the present invention.

In the hermetic-type compressor of the eleventh embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof will be omitted.

In FIG. 33, a valve plate 263 having a suction hole 273 is fixed to an end surface of the cylinder 10. One end of the suction passage 283 is disposed as an open end in the space inside the closed container 2, and the other end is substantially directly connected to the suction hole 273.

サ A suction lead 293 is attached to the valve plate 263 to open and close the suction hole 273.

軸 As shown in FIG. 33, the axial direction of the flow path in the connection portion of the suction flow path 283 to the suction hole 273 is inclined so as not to be perpendicular to the end face of the valve plate 263.

Next, the operation of the hermetic compressor according to the eleventh embodiment configured as described above will be described.

First, the case of the conventional hermetic compressor shown in FIG. 40 described in the background art will be described. In FIG. 40, the pressure wave (expansion wave) generated during the suction stroke becomes a reflected wave Wb (compression wave) whose phase is inverted in the space inside the closed container 2, and returns to the suction hole 19a. However, as shown in FIG. 40, the opening / closing surface of the suction lead 20 is at an angle close to perpendicular to the direction in which the reflected wave Wb travels, so that most of the reflected wave Wb is reflected on the suction lead 20 in almost the opposite direction. You. For this reason, in the conventional hermetic compressor, there is a problem that the pressure energy of the reflected wave Wb does not work effectively in the cylinder 10 and the supercharging effect cannot be sufficiently obtained.

In contrast, in the hermetic compressor according to the eleventh embodiment of the present invention shown in FIG. 33, the suction passage 273 is connected to the end face of the valve plate 263 not vertically but inclined. Therefore, as shown in FIG. 33, the reflected wave Wc directly enters the cylinder 10 without being reflected by the suction lead 293. Even when the reflected wave Wd is reflected by the suction lead 293, the angle between the traveling direction of the reflected wave Wd and the opening / closing surface of the suction lead 293 is small. Does not change significantly, and it easily enters the cylinder 10.

As described above, in the hermetic-type compressor of the eleventh embodiment, since the reflected wave is less likely to be obstructed by the suction lead 293, the pressure energy of the reflected wave enters the cylinder 10 effectively. The hermetic compressor of the eleventh aspect has a large refrigeration capacity.

(4) Since the angle formed between the direction in which the refrigerant gas to be sucked advances and the opening and closing surface of the suction lead 293 is small, the resistance of the flow of the refrigerant gas by the suction lead 293 also decreases, and the pressure loss decreases. Therefore, the hermetic-type compressor of Embodiment 11 has excellent refrigeration efficiency and high refrigeration capacity.

As described above, the hermetic compressor of the eleventh embodiment is inclined so that the axial direction of the flow path at the connection portion of the suction flow path 283 to the suction hole 273 is not perpendicular to the end face of the valve plate 263. It is configured. Therefore, the hermetic-type compressor of the eleventh embodiment has a configuration in which, when a reflected wave returns to the inside of the cylinder 10, the reflected wave easily enters the cylinder 10 directly without being reflected by the suction lead 293. Further, even when the reflected wave is reflected by the suction lead 293, the angle between the direction in which the reflected wave travels and the opening / closing surface of the suction lead 293 becomes small. Therefore, the traveling direction of the reflected wave after the reflection does not change significantly, and the reflected wave easily enters the cylinder 10. That is, the reflected wave is less likely to be disturbed by the suction lead 293, and the pressure energy of the reflected wave enters the cylinder 10 effectively. For this reason, the hermetic-type compressor of Embodiment 11 has excellent refrigeration efficiency and high refrigeration capacity.

(4) The resistance of the flow of the refrigerant gas sucked by the suction lead 293 is small, and the pressure loss is small. For this reason, the hermetic-type compressor of Embodiment 11 has higher refrigeration capacity.

(Embodiment 12)
Next, a twelfth embodiment which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 34 is a cross-sectional view showing the vicinity of the cylinder when the hermetic compressor according to Embodiment 12 of the present invention is stopped at a low outside air temperature. FIG. 35 is a cross-sectional view showing the vicinity of the cylinder when the hermetic-type compressor according to Embodiment 12 of the present invention is stopped at a high outside air temperature.

In the hermetic-type compressor of the twelfth embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof will be omitted.

34 and 35, a suction lead 304 is provided between the end face of the cylinder 10 and the valve plate 194. The suction lead 304 is configured to open and close the suction hole 194a of the valve plate 194. A deflection control mechanism 314 for controlling an initial deflection amount of the suction lead 304 is attached to the suction lead 304. In the twelfth embodiment, the deflection control mechanism 314 is formed of a material having a smaller linear expansion coefficient than that of the suction lead 304, and is fixed to the piston of the suction lead 304.

Next, the operation of the hermetic compressor of the twelfth embodiment configured as described above will be described.

Generally, at low outside temperatures, freezing and refrigeration equipment does not require large refrigeration capacity. However, in such a situation, if a conventional hermetic compressor supplies more refrigerant than necessary, the suction pressure will decrease and the discharge pressure will increase. As a result, there is a problem that the efficiency of the entire refrigeration system including the conventional hermetic compressor is reduced, and as a result, the total power consumption is increased.

を In order to solve this problem, the power consumption can be reduced by reducing the refrigerant circulation amount at low outside temperatures.

In the hermetic compressor of the twelfth embodiment, when the outside air temperature is low, the temperature of each part is generally low, and the temperatures of the suction lead 304 and the deflection control mechanism 314 are also low. In this case, as shown in FIG. 34, the suction lead 304 at the time of stoppage is in a state where the suction hole 194a is closed, that is, the initial deflection of the suction lead 304 is zero. In this state, the time from when the suction hole 194a is opened to when it is closed is shorter than when there is an initial deflection, and the displacement of the suction lead 304 is also smaller. Therefore, when the pressure wave generated during the suction stroke returns to the suction hole 194a as a reflected wave, the amount of the refrigerant gas sucked into the cylinder 10 is slightly reduced, and the effect of improving the refrigerant circulation amount due to supercharging is reduced. Become smaller. Therefore, the hermetic-type compressor of the twelfth embodiment can reduce power consumption at low outside air temperature.

At the time of high outside air temperature, the temperature of the suction lead 304 and the deflection control mechanism 314 also becomes high, and the deflection control mechanism 314 has a smaller linear expansion coefficient than the suction lead 304. Works like. As a result, as shown in FIG. 35, the suction lead 304 at the time of stoppage is in a state in which the suction hole 194a is opened, that is, a state in which the suction lead 304 has an initial deflection. In this state, the time from opening to closing of the suction hole 194a is longer than when the initial deflection is zero, and the displacement of the suction lead 304 is also larger. Therefore, when the pressure wave generated during the suction stroke returns to the suction hole 194a as a reflected wave, the amount of the refrigerant gas sucked into the cylinder 10 increases, and the effect of increasing the refrigerant circulation amount by the supercharging is sufficient. Is obtained. Therefore, the hermetic-type compressor of the twelfth embodiment has a sufficient effect of improving the refrigerating capacity due to the supercharging effect at a high outside temperature at which a large refrigerating capacity is required.

As described above, in the hermetic compressor according to the twelfth embodiment, the deflection control mechanism 314 for controlling the initial deflection amount of the suction lead 304 is formed of a material having a smaller linear expansion coefficient than the suction lead 304, and the piston of the suction lead 304 Is fixed to the side. For this reason, the hermetic-type compressor of the twelfth embodiment has a small refrigerating capacity improvement effect at low outside air temperature where a large refrigerating capacity is not required, thereby suppressing the power consumption. At the time of outside temperature, it is designed so that sufficient refrigeration capacity improvement effect can be obtained. For this reason, in the hermetic-type compressor of Embodiment 12, the total power consumption can be reduced by controlling the refrigeration capacity.

In the twelfth embodiment, the deflection control mechanism 314 is formed of a material having a smaller linear expansion coefficient than that of the suction lead 304 and is fixed to the piston of the suction lead 304. However, even if the deflection control mechanism 314 is made of a material having a larger linear expansion coefficient than the suction lead 304 and is fixed to the suction piston 304 on the side opposite to the piston, the same effect as that of the twelfth embodiment can be obtained.

(Embodiment 13)
Next, a thirteenth embodiment which is an example of the hermetic compressor of the present invention will be described with reference to the accompanying drawings.

FIG. 36 is a cross-sectional view showing the vicinity of the cylinder when the hermetic compressor according to Embodiment 13 of the present invention is stopped at a low outside air temperature. FIG. 37 is a cross-sectional view showing the vicinity of the cylinder when the hermetic-type compressor according to Embodiment 13 of the present invention is stopped at a high outside air temperature.

In the hermetic-type compressor of the thirteenth embodiment, those having the same functions and configurations as those of the hermetic-type compressor of each of the above-described embodiments are denoted by the same reference numerals, and description thereof will be omitted.

36 and 37, a suction lead 325 is provided between the end face of the cylinder 10 and the valve plate 195. The suction lead 325 is configured to open and close the suction hole 195a of the valve plate 195. In the thirteenth embodiment, a bending control mechanism 345 for controlling the initial bending amount of the suction lead 325 is attached. The deflection control mechanism 345 is made of a material that is deformed by temperature, such as bimetal or shape memory alloy, and is disposed in a through hole 195b formed in the valve plate 195. The deflection control mechanism 345 is provided so as to be able to expand and contract within the through hole 195b.

Next, the operation of the hermetic compressor of Embodiment 13 configured as described above will be described.

Generally, at low outside temperatures, freezing and refrigeration equipment does not require large refrigeration capacity. However, in such a situation, if a conventional hermetic compressor supplies more refrigerant than necessary, the suction pressure will decrease and the discharge pressure will increase. As a result, there is a problem that the efficiency of the entire refrigeration system including the conventional hermetic compressor is reduced, and as a result, the total power consumption is increased.

を In order to solve this problem, the power consumption can be reduced by reducing the refrigerant circulation amount at low outside temperatures.

In the hermetic compressor of the thirteenth embodiment, the temperature of each part is generally low when the outside air temperature is low, and the temperature of the deflection control mechanism 345 is also low. In this case, the deflection control mechanism 345 does not push up the suction lead 325, and the suction lead 325 when stopped does not close the suction hole 195a as shown in FIG. 36, that is, the initial deflection of the suction lead 325 is zero. It has become. In this state, the time from when the suction hole 195a is opened to when it is closed is shorter than when there is an initial deflection. Therefore, when the pressure wave generated during the suction stroke returns to the suction hole 195a as a reflected wave, the amount of the refrigerant gas sucked into the cylinder 10 is slightly reduced, and the effect of improving the refrigerant circulation amount due to supercharging is reduced. Become smaller. Therefore, the hermetic-type compressor of the thirteenth embodiment can reduce power consumption at low outside air temperature.

On the other hand, when the outside air temperature is high, the temperature of the deflection control mechanism 345 also increases, and the deflection control mechanism 345 extends to push up the suction lead 325. For this reason, as shown in FIG. 37, the suction lead 325 in the stop state is in a state where the suction hole 195a is opened, that is, a state where the suction lead 325 has an initial deflection. In this state, the time from when the suction hole 195a is opened to when it is closed is longer than when the initial deflection is zero. Therefore, when the pressure wave generated during the suction stroke returns to the suction hole 195a as a reflected wave, the amount of the refrigerant gas sucked into the cylinder 10 increases, and the effect of increasing the refrigerant circulation amount by the supercharging is sufficient. Is obtained.

Therefore, in the hermetic compressor of the thirteenth embodiment, when the outside air temperature requires a large refrigeration capacity, a sufficient improvement effect of the refrigeration capacity by the supercharging effect can be obtained.

As described above, in the hermetic compressor according to the thirteenth embodiment, the deflection control mechanism 345 that controls the initial deflection amount of the suction lead 325 is made of a bimetal or shape memory alloy or another material that is deformed by temperature. It is configured to be telescopically provided in the plate 195. For this reason, in the hermetic-type compressor of the thirteenth embodiment, the effect of improving the refrigerating capacity is small at a low outside air temperature where a large refrigerating capacity is not required, the power consumption is reduced, and the high refrigerating capacity requiring a large refrigerating capacity is reduced. At the time of temperature, sufficient refrigeration capacity improvement effect can be obtained. Therefore, the hermetic-type compressor of the thirteenth embodiment can reduce the total power consumption by controlling the refrigeration capacity.

As described above, the compressor according to the present invention is used in a refrigerator or the like, and drives the electric motor at two or more specific frequencies by the inverter device and completes the suction of the refrigerant gas. By increasing the pressure inside the cylinder above the low-pressure side pressure of the refrigeration cycle, the density of the refrigerant gas sucked into the cylinder is increased, and high refrigeration capacity is exhibited. This is used to configure a quiet refrigerating device or the like that prevents the generation of resonance noise and suppresses the generation of noise.

Sectional plan view for explaining general components of a hermetic compressor according to Embodiment 1 of the present invention. Longitudinal sectional view for explaining general components of a hermetic compressor according to Embodiment 1 of the present invention. 1 is a sectional plan view showing a hermetic compressor according to a first embodiment of the present invention. FIG. 1 is a control block diagram of a refrigeration apparatus including a hermetic compressor according to Embodiment 1 of the present invention. FIG. 3 is a characteristic diagram showing a change in refrigeration capacity during rotation speed control in the hermetic compressor according to the first embodiment of the present invention. Longitudinal sectional view of a hermetic compressor according to Embodiment 2 of the present invention. 6 is a front sectional view of the hermetic compressor shown in FIG. 6 according to a second embodiment of the present invention, taken along line EE. Longitudinal sectional view of a hermetic compressor according to Embodiment 3 of the present invention. Sectional plan view of a hermetic compressor according to Embodiment 3 of the present invention. Explanatory drawing of the behavior of the refrigerant gas in the hermetic compressor according to Embodiment 3 of the present invention. 4 is a longitudinal sectional view of a hermetic compressor according to Embodiment 4 of the present invention. 4 is a sectional plan view of a hermetic compressor according to Embodiment 4 of the present invention. A longitudinal sectional view of a hermetic compressor according to a fifth embodiment of the present invention. FIG. 13 is a cross-sectional view of the hermetic compressor according to the fifth embodiment of the present invention, taken along line BB of FIG. 13. 6 is a longitudinal sectional view of a hermetic compressor according to Embodiment 6 of the present invention. 15 is a cross-sectional view of the hermetic compressor according to the sixth embodiment of the present invention, taken along line CC of FIG. 6 is a characteristic diagram showing a change in a rise ratio of a suction pressure according to Embodiment 6 of the present invention. Characteristic diagram showing refrigeration capacity improvement ratio change in Embodiment 6 of the present invention Characteristic diagram showing noise change in Embodiment 6 of the present invention 7 is a longitudinal sectional view of a hermetic compressor according to Embodiment 7 of the present invention. Sectional drawing of the hermetic compressor according to the seventh embodiment of the present invention, taken along line DD in FIG. 7 is a longitudinal sectional view showing an open end of a first suction pipe according to a seventh embodiment of the present invention. The figure which shows the opening surface of the opening end part of the 1st suction pipe in Embodiment 7 of this invention. Longitudinal sectional view of a hermetic compressor according to an eighth embodiment of the present invention. FIG. 24 is a front sectional view of the hermetic compressor shown in FIG. 24 according to the eighth embodiment of the present invention, taken along line BB. Longitudinal sectional view of a hermetic-type compressor having another suction passage shape according to Embodiment 8 of the present invention. FIG. 26 is a sectional front view of the hermetic-type compressor shown in FIG. 26 according to an eighth embodiment of the present invention, taken along line CC. 9 is a longitudinal sectional view of a hermetic compressor according to a ninth embodiment of the present invention. FIG. 28 is a front sectional view of the hermetic compressor shown in FIG. 28 according to the ninth embodiment of the present invention, taken along line DD. Sectional plan view showing a hermetic compressor according to Embodiment 10 of the present invention. 30 is a front sectional view taken along line BB in FIG. 30. Sectional view showing the vicinity of a suction flow path of a hermetic-type compressor according to Embodiment 10. Sectional view showing the vicinity of a cylinder of a hermetic compressor according to Embodiment 11 of the present invention. Sectional view showing the vicinity of a cylinder when a hermetic compressor according to Embodiment 12 of the present invention is stopped at a low outside air temperature. Sectional view showing the vicinity of the cylinder when the hermetic-type compressor of Embodiment 12 is stopped at the time of high outside air temperature. Sectional view showing the vicinity of a cylinder when a hermetic-type compressor according to Embodiment 13 of the present invention is stopped at a low outside air temperature. Sectional view showing the vicinity of a cylinder when the hermetic-type compressor of Embodiment 13 is stopped at a high outside air temperature. Longitudinal cross-sectional view of a conventional hermetic compressor for noise reduction Cross-sectional plan view of a conventional hermetic compressor for noise reduction Longitudinal sectional view of a conventional hermetic compressor for improving the refrigeration capacity Sectional plan view of the hermetic compressor of FIG. Sectional view of the essential part of the hermetic compressor of FIG. 40 taken along line AA. Illustration of refrigerant gas behavior

Explanation of reference numerals

2 Closed container 6,300 Compression element 7,211 Motor 10 Cylinder 19,150,191,192,193,194,195,263 Valve plate 19a, 150a, 191a, 192a, 193a, 194a, 195a, 273 Suction hole 222, 283 Suction flow path 23, 193, 200, 229, 231 Suction pipe (suction flow path)
241 Suction muffler 212 Inverter device 11 Piston 12 Crankshaft 20,293,304,325 Suction lead 210 First suction pipe 190 Second suction pipe 201b Bend 232 Resonance type muffler 314,345 Deflection control mechanism

Claims (13)

A compression element for compressing the refrigerant and an electric motor for driving the compression element are housed in the closed container. The compression element includes a suction muffler, a cylinder, a suction hole communicating with the cylinder, and one end of the suction hole. And a suction flow path substantially open to the space in the closed container at the other end and substantially wrapped in the muffler, wherein the electric motor is driven by an inverter at two or more specific frequencies. Driven hermetic compressor. In the closed container, a compression element for compressing the refrigerant and an electric motor for driving the compression element are housed, and the compression element is a suction muffler, a cylinder, a piston reciprocating in the cylinder, and an end face of the cylinder. A valve plate disposed and having a suction hole communicating with the inside of the cylinder, one end of which is substantially directly connected to the suction hole, and the other end of which is open to a space in the closed container and substantially inside the muffler. A reciprocating hermetic compressor having an enclosed suction passage, wherein the electric motor is driven at two or more specific frequencies by an inverter device. In the closed container, a compression element for compressing the refrigerant and an electric motor for driving the compression element are housed, and the compression element is a suction muffler, a cylinder, a piston reciprocating in the cylinder, and an end face of the cylinder. A valve plate disposed and having a suction hole communicating with the inside of the cylinder, one end of which is substantially directly connected to the suction hole, and the other end of which is open to a space in the closed container and substantially inside the muffler. A suction flow path that is wrapped around, and the motor is driven at two or more specific frequencies by an inverter device, so that the refrigerating capacity changes and a pressure wave near the suction hole passes through the suction flow path. A reflected wave is formed at the opening end of the suction passage, and the reflected wave reaches the suction hole at the time of completion of the suction, thereby increasing the suction density of the refrigerant and improving the refrigerating capacity. By reciprocating hermetic compressor expand the scope of the refrigerating capacity. The compression element includes a crankshaft and a suction lead that opens and closes the suction hole, a crank angle at which the suction lead starts to open is θs (rad), a length of the suction passage is L (m), The rotational speed of the crankshaft is f (Hz), the sound speed of the refrigerant gas in the suction passage is As (m / sec), and the pressure wave generated in the suction hole at the start of suction is represented by the following (Equation 1). The hermetic compressor according to any one of claims 1 to 3, wherein the return crank angle θr (rad) is set in a range of the following (Equation 2).
θr = θs + 4π × L × f / As (1)
1.4 (rad) ≦ θr ≦ 3.0 (rad) (2) The hermetic seal according to any one of claims 1 to 3, wherein the compression element includes a crankshaft, and a resonance frequency of the refrigerant gas in the hermetic container is different from a frequency near an integral multiple of a rotation speed of the crankshaft. Type compressor. The hermetic compressor according to any one of claims 1 to 3, wherein at least a part of the suction channel is formed of a material having low thermal conductivity. The suction passage has a first suction pipe, and the second suction pipe has one end connected to the refrigeration cycle and the other end arranged as an open end near the open end of the first suction pipe. The hermetic compressor according to any one of claims 1 to 3. The hermetic compressor according to any one of claims 1 to 3, wherein the suction passage has a plurality of open ends, and the length from the suction hole to the open end is at least two or more. The hermetic compressor according to any one of claims 1 to 3, wherein the suction passage has a bent portion, and the bent portion has a substantially uniform curvature. The hermetic compressor according to any one of claims 1 to 3, wherein the suction flow path is bent a plurality of times and formed so as to be close to each other. The hermetic compressor according to any one of claims 1 to 3, wherein a resonance type muffler is formed in the suction passage. A suction lead for opening and closing the suction hole, wherein an axial direction of the suction flow path at a directly connected portion between the suction hole and the suction flow path has an angle smaller than 90 degrees with respect to a connection surface of the valve plate. The hermetic compressor according to claim 2 or 3, wherein: 4. The hermetic compressor according to claim 1, further comprising a suction lead that opens and closes the suction hole, and a deflection control mechanism that controls an initial deflection amount of the suction lead. 5.

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