JP2011196203A - Compressor and air conditioner - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor and an air conditioner, which reduce a suction pressure loss when a refrigerant in a compression vessel is sucked into compression mechanisms.SOLUTION: This compressor 4 includes a low-stage compression mechanism 50 and a high-stage compression mechanism 40 provided in a sealed vessel 10. The high-stage compression mechanism 40 has an annular cylinder 41 formed with a compression chamber 43 and a head member 42 arranged on the end surface of the cylinder 41. The cylinder 41 has a first suction passage 41d communicating with the compression chamber 43 while being inclined to be arranged radially inward as it is separated from the head member 42. The head member 42 has a second suction passage 42a arranged radially outward of the compression chamber 43 and allowing the first suction passage 41d to communicate with the refrigerant in a space S1 on a side opposite to the cylinder 41 with respect to the head member 42 in the sealed vessel 10. The refrigerant in the space S1 is sucked into the compression chamber 43 through the second suction passage 42a and first suction passage 41d.

Description

  The present invention relates to a compressor used in home appliances and the like, and an air conditioner to which the compressor is applied.

  As a conventional two-stage compression compressor, a compressor including a low-stage compression mechanism and a high-stage compression mechanism arranged in a casing is known (for example, see Patent Document 1). In this compressor, the low-pressure gas refrigerant can be sucked from the accumulator into the low-stage compression mechanism. The intermediate pressure gas refrigerant compressed by the low stage side compression mechanism is discharged to the primary space in the casing, and the intermediate pressure gas refrigerant discharged to the primary space is sucked into the high stage side compression mechanism. It has become. Then, the high-pressure gas refrigerant compressed by the high stage side compression mechanism is discharged to the outside of the casing.

Japanese Patent No. 4151120

  However, in the above-described two-stage compression compressor, the intermediate-pressure gas refrigerant compressed by the low-stage compression mechanism and discharged into the casing is sucked into the high-stage compression mechanism. Is sucked into the compression chamber of the high-stage compression mechanism through a flow path that bends at a right angle. Therefore, the pressure loss in the suction process to the high stage side compression mechanism becomes large, and as a result, the efficiency of the compressor is reduced.

  The objective of this invention is providing the compressor and air conditioner which can reduce the suction pressure loss at the time of suck | inhaling the refrigerant | coolant compressed with the low stage side compression mechanism to the high stage side compression mechanism.

  According to a first aspect of the present invention, there is provided a compressor including a low-stage compression mechanism and a high-stage compression mechanism provided in a hermetically sealed container, wherein the high-stage compression mechanism has an annular shape in which a compression chamber is formed. A cylinder and a head member disposed on an end surface of the cylinder, and the cylinder includes a first suction path that communicates with the compression chamber while being inclined so as to be disposed radially inward as the head member is separated from the cylinder; The head member is disposed radially outward from the compression chamber, and has a second suction path that allows the refrigerant in the space on the opposite side of the cylinder to the head member in the sealed container to communicate with the first suction path. The refrigerant in the space is sucked into the compression chamber through the second suction path and the first suction path.

  In this compressor, when configured as a two-stage compressor in which a high-stage compression mechanism and a low-stage compression mechanism are arranged in a hermetically sealed container, the cylinder has a head member at the end face of the cylinder where the head member is arranged. Since the first suction passage that is inclined so as to be arranged radially inward as the distance from the head is increased, the refrigerant in the space on the opposite side of the cylinder from the head member in the sealed container causes the second suction passage and The air is sucked into the compression chamber via the first suction passage while moving in an oblique direction (a direction inclined with respect to a plane perpendicular to the axial direction of the cylinder). Therefore, the suction pressure loss in the refrigerant suction process can be reduced as compared with the refrigerant sucked into the compression chamber while moving in the direction parallel to the end face of the cylinder.

  A compressor according to a second invention is the compressor according to the first invention, wherein the second suction path is formed along the axial direction of the cylinder, and the first suction path extends to the end surface of the cylinder. In addition, at the boundary between the cylinder and the head member, the radially outer end of the second suction path coincides with the radially outer end of the first suction path.

  In this compressor, the flow path in which the refrigerant in the space opposite to the cylinder with respect to the head member in the sealed container is directed toward the compression chamber of the cylinder can be gently bent from a right angle. Therefore, the suction pressure loss in the refrigerant suction process can be reduced as compared with the case where the refrigerant flow path is bent at a right angle.

  A compressor according to a third aspect is the compressor according to the first aspect, wherein the second suction path is inclined in a direction parallel to the first suction path, and the first suction path extends to the end surface of the cylinder. In the boundary between the cylinder and the head member, the radially outer end of the second suction path coincides with the radially outer end of the first suction path.

  In this compressor, the flow path in which the refrigerant in the space on the opposite side of the cylinder from the head member in the sealed container heads toward the compression chamber of the cylinder bends at the boundary between the first suction path and the second suction path. Therefore, it is possible to further reduce the suction pressure loss in the refrigerant suction process as compared with the case of bending at the boundary between the first suction path and the second suction path.

  According to a fourth aspect of the present invention, in the compressor according to any one of the first to third aspects, the corner on the inner peripheral side of the cylinder is arranged radially inward as the distance from the head member increases. A notch having an inclined surface extending to the compression chamber while being inclined to the compression chamber is provided as the first suction path.

  In this compressor, the first suction path can be formed only by cutting out the corner portion on the inner peripheral side of the cylinder, instead of forming the first suction path by subjecting the cylinder to complicated processing and providing a suction hole. Thus, the first suction path can be easily formed.

  A compressor according to a fifth aspect is the compressor according to the fourth aspect, wherein the radially inner end of the second suction passage is disposed radially outside the compression chamber at the boundary between the cylinder and the head member. Is done.

  In this compressor, the opening area of the first suction path is set to the compression chamber by arranging the radially inner end of the second suction path at the boundary between the cylinder and the head member. It can be gradually increased along the flow of the refrigerant. Therefore, the suction pressure loss in the refrigerant suction process can be further reduced.

  An air conditioner according to a sixth aspect uses the compressor according to any one of the first to fifth aspects.

  In this air conditioner, the same effects as those of the first to fifth inventions can be obtained.

  As described above, according to the present invention, the following effects can be obtained.

  In the first aspect of the invention, when the high-stage compression mechanism and the low-stage compression mechanism are configured as a two-stage compressor arranged in a sealed container, the cylinder includes a head on the end face of the cylinder where the head member is arranged. Since the first suction path is provided so as to be disposed radially inward as it is separated from the member, the refrigerant in the space on the opposite side of the cylinder from the head member in the sealed container causes the second suction path to And it is sucked into the compression chamber while moving in an oblique direction (a direction inclined with respect to a plane perpendicular to the axial direction of the cylinder) via the first suction path. Therefore, the suction pressure loss in the refrigerant suction process can be reduced as compared with the refrigerant sucked into the compression chamber while moving in the direction parallel to the end face of the cylinder.

  In the second invention, the flow path in which the refrigerant in the space on the opposite side of the cylinder from the head member in the sealed container heads toward the compression chamber of the cylinder can be gently bent from a right angle. Therefore, the suction pressure loss in the refrigerant suction process can be reduced as compared with the case where the refrigerant flow path is bent at a right angle.

  In the third invention, the flow path in which the refrigerant in the space opposite to the cylinder with respect to the head member in the sealed container is directed to the compression chamber of the cylinder is a boundary portion between the first suction path and the second suction path. Therefore, the suction pressure loss in the refrigerant suction process can be further reduced as compared with the case where the refrigerant is bent at the boundary between the first suction path and the second suction path.

  In the fourth aspect of the invention, the first suction passage is not formed by forming a suction hole by performing complicated processing on the cylinder but only by cutting out a corner portion on the inner peripheral side of the cylinder. Therefore, the first suction path can be easily formed.

  In the fifth aspect of the present invention, the opening area of the first suction passage is increased by disposing the end portion on the radially inner side of the second suction passage at the boundary between the cylinder and the head member on the radially outer side of the compression chamber. It can be gradually increased along the flow of the refrigerant toward the compression chamber. Therefore, the suction pressure loss in the refrigerant suction process can be further reduced.

  In the sixth invention, the same effect as in the first to fifth inventions can be obtained.

1 is a perspective view of an air conditioner according to a first embodiment of the present invention. It is a piping system diagram of an air conditioner. It is sectional drawing which showed the internal structure of the compressor shown in FIG. FIG. 4 is a top view of the high stage cylinder shown in FIG. 3. FIG. 4 is a top view of the front head shown in FIG. 3. FIG. 4 is a top view of the low-stage cylinder shown in FIG. 3. It is the figure which expanded the part enclosed with the dashed-dotted line of FIG. It is explanatory drawing which showed an example of the change of a total loss coefficient. It is sectional drawing which showed the internal structure of the compressor which concerns on 2nd Embodiment of this invention. FIG. 10 is a top view of the front head shown in FIG. 9. It is the figure which expanded the part enclosed with the dashed-dotted line of FIG. The total loss coefficient when the angle formed between the surface and the suction path is 45 ° is shown. It is sectional drawing which showed the internal structure of the compressor which concerns on 3rd Embodiment of this invention. It is the figure which expanded the part enclosed with the dashed-dotted line of FIG. It is sectional drawing which showed the internal structure of the compressor which concerns on 4th Embodiment of this invention. FIG. 16 is a top view of the high stage side cylinder shown in FIG. 15. It is the figure which expanded the part enclosed with the dashed-dotted line of FIG. It is explanatory drawing which showed the modification of the compressor which concerns on 4th Embodiment of this invention. It is explanatory drawing which showed the modification of the compressor which concerns on 4th Embodiment of this invention.

(First embodiment)
Hereinafter, a first embodiment of a compressor and an air conditioner according to the present invention will be described based on the drawings. FIG. 1 is a perspective view of an air conditioner according to a first embodiment of the present invention. FIG. 2 is a piping system diagram of the air conditioner.

[Overall configuration of air conditioner]
As shown in FIG. 1, the air conditioner 1 according to the first embodiment includes an indoor unit 1 a installed on an indoor wall surface, an outdoor unit 1 b installed outdoor, an indoor unit 1 a, and an outdoor unit 1 b. A connecting pipe 1c to be connected is provided, and equipment / valves housed in the indoor unit 1a and the outdoor unit 1b are connected to the connecting pipe 1c to form a refrigerant circuit. As shown in FIG. 2, the refrigerant circuit mainly includes an indoor heat exchanger 2, an outdoor heat exchanger 3, a compressor 4, and an electric expansion valve 5. Thereby, the high temperature / high pressure refrigerant discharged from the compressor 4 flows into the outdoor heat exchanger 3 during the cooling operation.

The CO ₂ refrigerant condensed in the outdoor heat exchanger 3 (hereinafter abbreviated as “refrigerant”) is decompressed by the electric expansion valve 5 and then flows into the indoor heat exchanger 2. Then, the refrigerant evaporated in the indoor heat exchanger 2 returns to the suction side of the compressor 4. In this way, the air around the indoor heat exchanger 2 is cooled and cold air is supplied indoors. Further, during the heating operation, the high-temperature and high-pressure refrigerant discharged from the compressor 4 flows into the indoor heat exchanger 2. Then, the refrigerant condensed in the indoor heat exchanger 2 is decompressed by the electric expansion valve 5 and then flows into the outdoor heat exchanger 3. Then, the refrigerant evaporated in the outdoor heat exchanger 3 returns to the suction side of the compressor 4. In this way, the air around the indoor heat exchanger 2 is heated and hot air is supplied indoors.

[Indoor units and outdoor units]
As shown in FIG. 2, the indoor unit 1 a mainly includes an indoor heat exchanger 2 and an indoor fan 6 attached to the indoor heat exchanger 2. The outdoor unit 1b includes a two-stage compression compressor 4, a four-way switching valve 7 connected to the discharge side of the compressor 4, an accumulator 8 connected to the suction side of the compressor 4, and a four-way switching valve. 7, an outdoor heat exchanger 3 connected to 7, an electric expansion valve 5 connected to the outdoor heat exchanger 3, and an outdoor fan 9 attached to the outdoor heat exchanger 3. The electric expansion valve 5 is connected to one end of the indoor heat exchanger 2 through a liquid refrigerant pipe. The four-way switching valve 7 is connected to the other end of the indoor heat exchanger 2 through a gas refrigerant pipe. The liquid refrigerant pipe and the gas refrigerant pipe correspond to the connection pipe 1c described above.

[Compressor configuration]
FIG. 3 is a cross-sectional view showing the internal structure of the compressor shown in FIG. 4 to 6 are top views of the high-stage cylinder, the front head, and the low-stage cylinder shown in FIG. As shown in FIG. 3, the compressor 4 configured in a two-stage compression type includes a motor 20 and a compression mechanism 30 disposed below the motor 20 in a hermetic casing (sealed container) 10. The compression mechanism 30 includes a high-stage compression mechanism 40, a low-stage compression mechanism 50 disposed below the high-stage compression mechanism 40, a high-stage compression mechanism 40, and a low-stage compression mechanism 40. It is comprised by the middle plate 60 arrange | positioned between the stage side compression mechanisms 50. FIG.

[Composition of casing]
As shown in FIG. 3, the casing 10 includes a top 11, a pipe 12, and a bottom 13 for forming a sealed space. The top 11 is provided as a member that closes the opening at the upper end of the pipe 12, and a terminal terminal 11 a connected to the motor 20 is provided on the top 11. A suction hole 12a and a discharge hole 12b for introducing the inlet tubes 80a and 80b into the casing 10 are respectively formed on both side surfaces of the pipe 12, and the low pressure gas refrigerant is supplied from the accumulator 8 through the suction hole 12a. The high-pressure gas refrigerant can be discharged toward the four-way switching valve 7 through the discharge hole 12b. In addition, joint pipes 90a and 90b formed in a cylindrical shape for joining the inlet tubes 80a and 80b are joined to the inner peripheral surfaces of the suction hole 12a and the discharge hole 12b, respectively. The bottom 13 is provided as a member that closes the opening at the lower end of the pipe 12, and an oil reservoir 70 for storing lubricating oil is provided therein.

[Motor configuration]
As shown in FIG. 3, the motor 20 includes a stator 21 fixed to the inner peripheral surface of the casing 10, a rotor 22 disposed inside the stator 21, and a drive shaft 23 connected to the center portion of the rotor 22. The drive shaft 23 is connected to both the high stage side compression mechanism 40 and the low stage side compression mechanism 50. The lower end portion of the drive shaft 23 is immersed in the oil reservoir 70, and the lubricating oil stored in the oil reservoir 70 is supplied to each slide of the compression mechanism 30 through an oil supply passage formed in the drive shaft 23. It can be supplied to the moving part.

[Configuration of high-stage compression mechanism]
As shown in FIG. 3, the high-stage compression mechanism 40 includes a high-stage cylinder 41 (cylinder) and a front head 42 (head member) disposed above the high-stage cylinder 41. A high-stage compression chamber 43 (compression chamber), which will be described later, of the high-stage cylinder 41 is closed by the front head 42. A primary space (space) R <b> 1 is formed on the opposite side of the front stage 42 in the casing 10 from the high-stage cylinder 41.

[Configuration of high-stage cylinder]
As shown in FIG. 4, the high stage side cylinder 41 is formed in an annular shape in plan view, and a high stage side compression chamber 43 is provided on the radially inner side. Inside the high-stage compression chamber 43 is accommodated a high-stage piston 44 in which a roller 44 a and a blade 44 b are integrated, and a drive shaft 23 is disposed radially inside the high-stage piston 44. The mounted eccentric shaft part 45 is rotatably fitted. The eccentric shaft portion 45 is formed eccentrically with respect to the drive shaft 23, and the roller 44 a is configured to be capable of performing an eccentric motion in the high-stage side cylinder chamber 43 as the drive shaft 23 rotates. The high-stage compression chamber 43 is partitioned by a blade 44b into a low-pressure chamber LB1 that sucks refrigerant and a high-pressure chamber HB1 that compresses the drawn refrigerant. A holding hole 46 is formed outside the high stage compression chamber 43. The inside of the holding hole 46 is partitioned into a low pressure chamber LB1 side and a high pressure chamber HB1 side by a blade 44b. A low pressure chamber side bush 47 and a high pressure chamber side bush 48 are disposed on the holding hole 46 on the low pressure chamber LB1 side and the high pressure chamber HB1 side, respectively.

  As shown in FIGS. 3 and 4, the high-stage cylinder 41 is formed with a notch 41 a, a communication path 41 b, and a discharge path 41 c on the outer side in the radial direction than the high-stage compression chamber 43. As shown in FIG. 3, the notch portion 41 a is compressed at a high stage side while being inclined so as to be arranged radially inward as the distance from the front head 42 is increased at the corner on the inner peripheral side of the high stage side cylinder 41. It is formed as an inclined surface extending to the chamber 43. The notch 41a extends to the end surface of the high-stage cylinder 41, and the formation of the notch 41a forms a suction passage 41d that communicates with the high-stage compression chamber 43. Yes.

  As shown in FIG. 3, the communication passage 41 b is formed so as to penetrate the inside of the high-stage cylinder 41 along the axial direction of the drive shaft 23. The communication path 41b communicates with the discharge path 51b formed in the low-stage cylinder 51 together with the communication path 42b formed in the front head 42 and the communication path 60a formed in the middle plate 60, thereby reducing the primary space R1 and An intermediate passage IP that communicates with the lower stage compression chamber 53 of the stage side cylinder 51 is configured. Therefore, the intermediate-pressure gas refrigerant compressed in the low-stage side compression chamber 53 is configured to be discharged into the primary space R1 through the intermediate passage IP. As shown in FIG. 4, the discharge path 41 c is formed so as to penetrate from the high-stage side compression chamber 43 toward the radially outer side in a plan view. The discharge passage 41c is provided with a discharge valve (not shown) that opens a discharge port when a predetermined pressure is reached, and the end opposite to the high-stage compression chamber 43 is shown in FIG. As described above, the high-pressure gas refrigerant compressed in the high-stage compression chamber 43 can be discharged toward the four-way switching valve 7 through the discharge hole 12 through the inlet tube 80b. It has a configuration.

[Configuration of front head]
As shown in FIG. 5, the front head 42 is formed with a suction path (second suction path) 42 a and a communication path 42 b on the outer side in the radial direction than the drive shaft 23. As shown in FIG. 3, the suction path 42a is formed along the axial direction of the drive shaft 23, and the suction path 42a forms a primary space R1 and a suction path 41d formed in the high-stage cylinder 41. Communicate. By such communication, the intermediate-pressure gas refrigerant compressed in the low-stage compression chamber 53 and once discharged into the primary space R1 through the intermediate passage IP is directed from the primary space R1 to the high-stage compression chamber 43. Thus, an inhalable flow path is formed. Further, as shown in FIG. 3, the communication path 42b is formed through the interior of the front head 42 along the axial direction of the drive shaft 23, and constitutes an intermediate path IP together with the communication path 41b and the communication path 60a. The intermediate pressure gas refrigerant compressed in the low-stage compression chamber 53 can be discharged to the primary space R1 through the intermediate passage IP.

  3 indicates the flow of the intermediate-pressure gas refrigerant that is compressed in the low-stage compression chamber 53 and discharged toward the primary space R1 along the axial direction of the drive shaft 23 via the intermediate passage IP. Showing the road. Further, an arrow A2 in FIG. 3 indicates an intermediate-pressure gas refrigerant that is sucked from the primary space R1 into the suction passage 42a along the axial direction of the drive shaft 23 and sucked to the high-stage compression chamber 43 through the suction passage 41d. The flow path is shown.

[Configuration of low-stage compression mechanism]
As shown in FIG. 3, the low-stage compression mechanism 50 includes a low-stage cylinder 51 and a rear head 52 disposed below the low-stage cylinder 51. The end face is closed by the rear head 52.

[Low-stage cylinder configuration]
As shown in FIG. 6, the low-stage cylinder 51 is formed in an annular shape in plan view, and a low-stage compression chamber 53 is provided on the radially inner side. The low-stage compression chamber 53 contains a low-stage piston 54 integrally formed with a roller 54a and a blade 54b. The low-stage piston 54 has a drive shaft on the radially inner side. An eccentric shaft portion 55 to which 23 is attached is fitted rotatably. The eccentric shaft portion 55 is formed eccentrically with respect to the drive shaft 23, and is disposed at a position shifted by 180 ° in the rotation direction of the drive shaft 23 with respect to the eccentric shaft portion 45 of the high-stage side cylinder 41. . As a result, the roller 54a is configured to be capable of performing an eccentric motion within the low-stage compression chamber 53 as the drive shaft 23 rotates. The low-stage compression chamber 53 is partitioned by a blade 54b into a low-pressure chamber LB2 that sucks refrigerant and a high-pressure chamber HB2 that compresses the drawn refrigerant. A holding hole 56 is formed outside the low-stage compression chamber 53. The inside of the holding hole 56 is partitioned into a low pressure chamber LB2 side and a high pressure chamber HB2 side by a blade 54b. And the low pressure chamber side bush 57 and the high pressure chamber side bush 58 are arrange | positioned at the low pressure chamber LB2 side and the high pressure chamber HB2 side of the holding hole 56, respectively.

  As shown in FIGS. 3 and 6, the low-stage cylinder 51 is formed with a suction passage 51 a and a discharge passage 51 b communicating with the low-stage compression chamber 53 on the radially outer side of the low-stage compression chamber 53. Has been. As shown in FIG. 3, the suction passage 51 a is formed through the inside of the low-stage side cylinder 51 along the direction perpendicular to the axial direction of the drive shaft 23, and is opposite to the low-stage side compression chamber 53. The end on the side is connected to the suction hole 12a via the inlet tube 80a.

  Accordingly, the low-pressure gas refrigerant discharged from the accumulator 8 can be sucked up to the low-stage compression chamber 53 through the suction hole 12a. The discharge passage 51b is provided with a discharge valve (not shown) that opens a discharge port when a predetermined pressure is reached, and is bent at a substantially right angle inside the low-stage cylinder 51 as shown in FIG. By doing so, it communicates with the communication passage 60 formed in the middle plate 60, and the intermediate pressure gas refrigerant compressed in the low-stage compression chamber 53 can be discharged to the primary space R1 via the intermediate passage IP. ing.

FIG. 7 is an enlarged view of a portion surrounded by a one-dot chain line in FIG. Here, for convenience of explanation, illustration of the roller 44a and the eccentric shaft portion 45 is omitted. The sign theta ₁ in Figure 7, the radially outer end of the suction passage 42a, an angle at which the inclined surface is formed of the notch 41a, the intermediate directed from the primary space R1 on the higher-stage compression chamber 43 The bending angle at the boundary between the suction passages 42a and 41d for the pressurized gas refrigerant is shown. The sign theta ₂ in FIG. 7 shows an axial plane perpendicular S1 of the drive shaft 23 (one-dot chain line in FIG. 7), the inclined surface and the angle formed by the notch portion 41a. Note that these angles θ _{1 and} θ ₂ are both acute angles and are designed to be 90 ° in total.

  Further, as indicated by a one-dot chain line S <b> 2 in FIG. 7, at the boundary between the high stage side cylinder 41 and the front head 42, the radially inner end O <b> 1 of the suction path 42 a is larger in diameter than the high stage side compression chamber 43. At the boundary, the radially outer end O2 of the suction passage 42a coincides with the radially outer end O2 of the notch 41a.

Next, a method for calculating the total loss coefficient ζ ₀ and the total suction pressure loss h ₀ of the intermediate-pressure gas refrigerant passing through the suction path 42 a formed in the front head 42 and the suction path 41 d formed in the high-stage cylinder 41 will be described. To do. Note that the total loss factor zeta ₀ has a loss factor zeta ₁ when intermediate pressure gas refrigerant is sucked into the suction passage 41d from the intake passage 42a, an intermediate-pressure gas refrigerant in the high-stage compression chamber 43 from the suction passage 41d The sum of the loss coefficient ζ ₂ when inhaled is shown. These loss coefficients ζ ₁ and ζ ₂ can be obtained by substituting the angles θ ₁ and θ ₂ described above into the following equation (1), respectively, and the following equations (2) and (3) Can be expressed as
ζ = 0.946sin ² (θ / 2) + 2.05sin ⁴ (θ / 2) (1)
^{_{ζ 1 = 0.946sin 2 (θ 1}} /2)+2.05sin 4 (θ 1/2) ···· (2)
^{_{ζ 2 = 0.946sin 2 (θ 2}} /2)+2.05sin 4 (θ 2/2) ···· (3)

The total loss coefficient ζ ₀ can be obtained by adding these loss coefficients ζ ₁ and ζ ₂ and can be expressed by the following equation (4).
ζ ₀ = ζ ₁ + ζ ₂ (4)

Further, a suction pressure loss h ₁ when the intermediate-pressure gas refrigerant is sucked into the suction passage 41d from the intake passage 42a, the suction pressure loss h when intermediate pressure gas refrigerant is sucked into the high-stage compression chamber 43 from the suction passage 41d ₂ can be obtained by substituting the loss coefficients ζ ₁ and ζ ₂ shown in the above equations (2) and (3) into the following equation (5), and the following equations (6) and (7 ) Respectively. In equation (5), symbol ζ represents a loss coefficient, symbol ν represents fluid velocity, and symbol g represents gravitational acceleration.
h = ζ · ν ² / 2g (5)
^{_{h 1 = ζ 1 · ν 2}} / 2g ···· (6)
^{_{h 2 = ζ 2 · ν 2}} / 2g ···· (7)

The total suction pressure loss h ₀ can be obtained by adding the suction pressure losses h _{1 and} h ₂ and can be expressed by the following equation (8).

h ₀ = h ₁ + h ₂ = (ζ ₁ + ζ ₂ ) · ν ² / 2g = ζ ₀ · ν ² / 2g (8)
As is apparent from this equation (8), the total suction pressure loss h ₀ and the total loss coefficient ζ ₀ (= ζ ₁ + ζ ₂ ) are proportional to each other, and the total suction pressure loss h ₀ is the total loss coefficient. Increases / decreases as ζ ₀ increases / decreases.

FIG. 8 is an explanatory diagram showing an example of a change in the total loss coefficient. 8 represents the total loss coefficient ζ ₀ , and the horizontal axis in FIG. 8 represents the bending angle at the boundary between the suction passages 42 a and 41 d for the intermediate-pressure gas refrigerant from the primary space R 1 to the high-stage compression chamber 43. Degree θ ₁ is shown. As shown in FIG. 8, the total loss coefficient ζ ₀ has a maximum value (about 3.0) when the bending angle θ _{1 is set} to 0 °, and the suction pressure loss h that is proportional to the total loss coefficient ζ _{0. 0} also indicates the maximum value. When the bending angle θ ₁ is an acute angle (0 ° <θ ₁ <90 °), as shown in FIG. 8, the total loss coefficient ζ ₀ gradually increases as compared to the case where the bending angle θ ₁ is 0 °. When the bending angle θ ₁ is 45 °, the minimum value (about 2.0) is shown, and accordingly, the total suction pressure loss h ₀ also shows the minimum value. Then, the total loss factor zeta ₀ increases slowly as the skew angle theta ₁ is greater than 45 °, if the skew angle theta ₁ was 90 °, that is, as in the prior art, from the primary space R1 higher stage When the flow path of the intermediate-pressure gas refrigerant toward the side compression chamber 43 is bent at a right angle, the maximum value (3.0) is shown, and the total suction pressure loss h ₀ also shows the maximum value.

[Features of the air conditioner of the first embodiment]
As described above, in the air conditioner 1 of the first embodiment, the front head 42 is disposed when the high-stage compression mechanism 40 and the low-stage compression mechanism 50 are configured as a two-stage compressor disposed in the casing 10. On the end surface of the high-stage cylinder 41, a notch 41a is provided on the inner peripheral side of the high-stage cylinder 41 so as to be disposed radially inward as the head member is separated. The intermediate-pressure gas refrigerant compressed by the side compression mechanism 50 and discharged into the space on the opposite side of the high-stage cylinder 41 with respect to the front head 42 in the casing 10 passes through the second suction path 42a and the first suction path 41d. Via, it is sucked into the high-stage compression chamber 43 while moving in an oblique direction (a direction inclined with respect to a plane perpendicular to the axial direction of the high-stage cylinder 41). Therefore, compared to a case where the flow path of the intermediate pressure gas refrigerant is bent at a right angle, or a case where the intermediate pressure gas refrigerant is sucked into the high stage side compression chamber 43 while moving in a direction parallel to the end face of the high stage side cylinder 41. Thus, the suction pressure loss during the suction process of the intermediate pressure gas refrigerant can be further reduced.

  Further, in the air conditioner 1 of the first embodiment, the intake passage is not formed by performing complicated processing on the high stage side cylinder 41 and providing a suction hole, but on the inner peripheral side of the high stage side cylinder 41. Since the suction path 41d can be formed only by cutting out the corner, the suction path 41d can be easily formed.

  In the air conditioner 1 of the first embodiment, the radially inner end O1 of the suction passage 42a is radially outer than the high stage compression chamber 43 at the boundary between the high stage cylinder 41 and the front head 42. Accordingly, the opening area of the suction passage 41d can be gradually increased along the flow of the intermediate-pressure gas refrigerant toward the high-stage compression chamber 43. Accordingly, it is possible to further reduce the suction pressure loss in the suction process of the intermediate pressure gas refrigerant.

(Second Embodiment)
Hereinafter, a second embodiment of an air conditioner according to the present invention will be described based on the drawings. FIG. 9 is a cross-sectional view showing the internal structure of the compressor according to the second embodiment of the present invention. FIG. 10 is a top view of the front head shown in FIG. In this embodiment, the same elements as those described in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the compressor 104 of this embodiment, as shown in FIGS. 9 and 10, the front head 142 of the high-stage compression mechanism 140 of the compression mechanism 130 approaches the high-stage cylinder 41 of the high-stage compression mechanism 140. An inclined suction path (second suction path) 142a is formed so as to be disposed radially inward (as it goes downward), and is different from the compressor 4 of the first embodiment.

  As shown in FIG. 9, the primary space R <b> 1 and the suction path 41 d formed in the high-stage cylinder 41 communicate with each other through the suction path 142 a. By such communication, the intermediate-pressure gas refrigerant compressed in the low-stage compression chamber 53 and once discharged into the primary space R1 through the intermediate passage IP is sucked from the primary space R1 toward the high-stage compression chamber 43. A possible flow path A3 is formed.

FIG. 11 is an enlarged view of a portion surrounded by a one-dot chain line in FIG. Here, for convenience of explanation, illustration of the roller 44a and the eccentric shaft portion 45 is omitted. Further, reference sign θ ₃ in FIG. 11 indicates an angle formed by a surface S1 (a dashed line in FIG. 11) perpendicular to the axial direction of the drive shaft 23 and the suction path 142a, and this angle θ ₃ is an acute angle. Designed to. Further, as indicated by a one-dot chain line S2 in FIG. 11, at the boundary between the high stage side cylinder 41 and the front head 142, the radially inner end O3 of the suction passage 142a is in the radial direction of the high stage side compression chamber 43. The suction passage 142a is inclined in a direction parallel to the suction passage 41d and coincides with the outer end portion O3, and a radially outer end portion O4 of the suction passage 142a is formed in the high-stage cylinder 41. The cutout portion 41a is disposed on substantially the same plane. When the suction passage 142 a is disposed radially outside the high-stage compression chamber 43, the radially inner end of the suction passage 142 a coincides with the radially outer end of the high-stage compression chamber 43. The case where it does is included.

Next, a calculation method of the total loss coefficient ζ ₀ and the total suction pressure loss h ₀ of the intermediate pressure gas refrigerant passing through the suction path 142a formed in the front head 42 and the suction path 41d formed in the high-stage cylinder 41 will be described. To do. First, the total loss coefficient ζ ₀ can be obtained by substituting the angle θ ₃ described above into the above-described equation (1), and can be represented by the following equation (9).
^{_{ζ 0 = 0.946sin 2 (θ 3}} /2)+2.05sin 4 (θ 3/2) ···· (9)

The total suction pressure loss h ₀ can be obtained by substituting the total loss coefficient ζ ₀ shown in the above formula (9) into the above-described formula (5), and can be expressed by the following formula (10). .
^{_{h 0 = ζ 0 · ν 2}} / 2g ···· (10)

Figure 12 shows a total loss coefficient when the angle theta ₃ formed by the surface S1 and the suction passage 142a has a 45 °. The vertical axis in FIG. 12 represents the total loss coefficient ζ ₀ , and the horizontal axis in FIG. 12 represents the angle θ ₃ . As shown in FIG. 12, the total loss coefficient ζ ₀ shows a value of 1.0 when the angle θ ₃ is 45 ° (see point P1 in the figure), and when the angle θ ₃ is 90 °, That is, the maximum value (3.0) is shown when the flow of the intermediate-pressure gas refrigerant from the primary space R1 toward the high-stage compression chamber 43 is bent at a right angle as in the prior art (see point P2 in the figure). . As is apparent from these values, in this second embodiment, the total loss coefficient ζ ₀ can be suppressed to 1/3 of the conventional _value, and the total suction pressure loss h ₀ that is proportional to the total loss coefficient ζ _0. Can also be reduced to 1/3 of the conventional one.

[Features of the air conditioner of the second embodiment]
As described above, in the air conditioner according to the second embodiment, the flow path of the intermediate pressure gas refrigerant from the primary space R1 toward the high stage side compression chamber 43 of the high stage side cylinder 41 is the boundary portion between the suction paths 142a and 41d (see FIG. 11), the intermediate-pressure gas refrigerant can be sucked into the high-stage compression chamber 43 while moving in an oblique direction. Accordingly, the intermediate pressure gas refrigerant bent at the boundary portion of the suction passage or the intermediate pressure gas refrigerant is sucked into the high stage compression chamber 43 while moving in a direction parallel to the end surface of the high stage cylinder 41. In comparison with the above, the suction pressure loss in the suction process of the intermediate pressure gas refrigerant can be further reduced.

(Third embodiment)
Hereinafter, based on drawing, 3rd Embodiment of the air conditioner concerning this invention is described. FIG. 13 is a cross-sectional view showing the internal structure of the compressor according to the third embodiment of the present invention. In this embodiment, the same elements as those described in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the compressor 204 of this embodiment, as shown in FIG. 13, the front head 242 of the high-stage compression mechanism 240 of the compression mechanism 230 approaches the high-stage cylinder 41 of the high-stage compression mechanism 240 (downward). The suction path (second suction path) 242a is formed so as to be disposed radially inward, and is different from the compressor 4 of the first embodiment.

  As shown in FIG. 13, the primary space R <b> 1 and the suction path 41 d formed in the high-stage cylinder 41 communicate with each other through the suction path 242 a. By such communication, the intermediate-pressure gas refrigerant compressed in the low-stage compression chamber 53 and once discharged into the primary space R1 via the intermediate passage IP is directed from the primary space R1 toward the high-stage compression chamber 43. An inhalable flow path A4 is formed.

FIG. 14 is an enlarged view of a portion surrounded by a one-dot chain line in FIG. Here, for convenience of explanation, illustration of the roller 44a and the eccentric shaft portion 45 is omitted. The sign theta ₄ in FIG. 14, perpendicular to the axial direction surface S1 of the drive shaft 23 indicates the angle between the suction passage 242a makes with the (one-dot chain line in FIG. 14), the angle theta ₄ is an acute angle Designed. Further, as indicated by a one-dot chain line S <b> 2 in FIG. 14, at the boundary between the high stage side cylinder 41 and the front head 242, the radially inner end portion O <b> 5 of the suction path 242 a In addition to being disposed on the outer side in the direction, the radially outer end O6 of the suction path 242a is disposed on substantially the same plane as the notch 41a formed in the high-stage cylinder 41.

[Features of the air conditioner of the third embodiment]
As described above, in the air conditioner of the third embodiment, the flow path of the intermediate pressure gas refrigerant from the primary space R1 toward the high stage side compression chamber 43 of the high stage side cylinder 41 is the boundary portion between the suction paths 242a and 41d (see FIG. 14), the intermediate-pressure gas refrigerant can be sucked into the high-stage compression chamber 43 while moving in an oblique direction. Accordingly, the intermediate pressure gas refrigerant bent at the boundary portion of the suction passage or the intermediate pressure gas refrigerant is sucked into the high stage compression chamber 43 while moving in a direction parallel to the end surface of the high stage cylinder 41. In comparison with the above, the suction pressure loss in the suction process of the intermediate pressure gas refrigerant can be further reduced.

  In the air conditioner of the third embodiment, the radially inner end O5 of the suction passage 242a is disposed on the radially outer side of the higher stage compression chamber 43 at the boundary between the higher stage cylinder 41 and the front head 242. Thus, the opening area of the suction passage 41d can be gradually increased along the flow of the intermediate pressure gas refrigerant. Therefore, the suction pressure loss of the intermediate pressure gas refrigerant can be further reduced.

(Fourth embodiment)
Hereinafter, based on drawing, 4th Embodiment of the air conditioner which concerns on this invention is described. FIG. 15 is a cross-sectional view showing the internal structure of the compressor according to the fourth embodiment of the present invention. FIG. 16 is a top view of the high-stage cylinder shown in FIG. In this embodiment, the same elements as those described in the first embodiment are denoted by the same reference numerals, and detailed description thereof is omitted.

  In the compressor 304 of this embodiment, as shown in FIGS. 15 and 16, the inner peripheral side of the high-stage side cylinder 341 of the high-stage side compression mechanism 340 of the compression mechanism 330 is not cut out and processed on the high-stage side. It differs from the compressor 4 of 1st Embodiment by the point which formed the suction path (1st suction path) 341d in the inner peripheral side of the cylinder 341. FIG. The suction path 341d has inclined surfaces 341a and 341b that extend to the higher-stage compression chamber 43 while being inclined so as to be arranged radially inward as the distance from the front head 42 increases. The suction passage 341 d extends to the end surface of the high stage side cylinder 341 and communicates with the high stage side compression chamber 43. A flow path A4 that can be sucked from the primary space R1 toward the high-stage compression chamber 43 is formed.

FIG. 17 is an enlarged view of a portion surrounded by a one-dot chain line in FIG. Code theta ₁ in the figure shows the radially outer end of the suction passage 42a, the angle between the inclined surface 341a is. Code theta ₂ in the drawing, the axial plane perpendicular S1 of the drive shaft 23 indicates the angle between the inclined surface 341a is. As indicated by a one-dot chain line S2 in the drawing, the end portion O1 on the radially inner side of the suction passage 42a is located radially outside the high-stage compression chamber 43 at the boundary between the high-stage cylinder 341 and the front head 42. It arrange | positions and corresponds with the edge part O1 of the radial direction outer side of the inclined surface 341b. At this boundary, the radially outer end O2 of the suction passage 42a coincides with the radially outer end O2 of the inclined surface 341a.

[Features of the air conditioner of the fourth embodiment]
As mentioned above, in the air conditioner of 4th Embodiment, the effect similar to the air conditioner 1 of 1st Embodiment can be acquired.

  As mentioned above, although embodiment of this invention was described based on drawing, it should be thought that a specific structure is not limited to these embodiment. The scope of the present invention is indicated not only by the above description of the embodiments but also by the scope of claims for patent, and further includes all modifications within the meaning and scope equivalent to the scope of claims for patent.

  In the above-described fourth embodiment, the example in which the suction path 42a is formed along the axial direction of the drive shaft 23 in the front head 42 has been described, but the present invention is not limited to such an embodiment. As shown in FIG. 18, the front head 342 may be formed so as to be inclined so as to be disposed radially inward as the suction path 342 a approaches the high-stage side cylinder 341. Thereby, the effect similar to the air conditioner of 2nd Embodiment can be acquired. Further, a flat surface 341c perpendicular to the axial direction of the drive shaft 23 as shown in FIG. 19 may be formed on the radially inner portion of the inclined surface 341b of the high-stage cylinder 341 shown in FIG. Thereby, the effect similar to the air conditioner of 3rd Embodiment can be acquired.

  In the first to fourth embodiments described above, the example in which the low-stage compression mechanism 50 is disposed below the high-stage compression mechanisms 40 to 340 in the compression mechanisms 30 to 330 has been described. It is not limited to the embodiment. In the compression mechanisms 30 to 330, the low stage compression mechanism 50 may be disposed above the high stage compression mechanisms 40 to 340.

In the first to fourth embodiments described above, the compressor using the CO ₂ refrigerant has been described, but the present invention is not limited to such an embodiment. The present invention can also be applied to a compressor that uses a refrigerant other than the CO ₂ refrigerant.

  In the first to fourth embodiments described above, the example in which the roller and the blade are integrally formed in the high-stage piston of the high-stage cylinder and the low-stage piston of the low-stage cylinder has been described, but the present invention is applied. It is not limited to the embodiment. These rollers and blades may be configured separately.

  By using the present invention, it is possible to obtain a compressor and an air conditioner that can reduce the suction pressure loss when the refrigerant in the compression container is sucked into the compression mechanism.

1 Air conditioner 4, 104, 204, 304 Compressor 10 Casing (sealed container)
40, 140, 240, 340 High-stage compression mechanism 41, 341 High-stage cylinder (cylinder)
41d, 341d Suction path (first suction path)
42, 142, 242 and 342 Front head (head member)
42a, 142a, 242a, 342a Suction path (second suction path)
43 High-stage compression chamber (compression chamber)
50 Lower stage compression mechanism S1 Primary space (space)

Claims (6)

In a compressor provided with a low-stage compression mechanism and a high-stage compression mechanism provided in a sealed container,
The high stage compression mechanism is
An annular cylinder formed with a compression chamber;
A head member disposed on an end surface of the cylinder,
The cylinder has a first suction path that communicates with the compression chamber while being inclined so as to be arranged radially inward as the head member is separated from the head member;
The head member is disposed radially outside the compression chamber, and communicates the refrigerant in the space opposite to the cylinder with respect to the head member in the sealed container and the first suction path. Has two suction paths,
The refrigerant in the space is sucked into the compression chamber through the second suction passage and the first suction passage. The second suction path is formed along the axial direction of the cylinder,
The first suction passage extends to an end face of the cylinder;
2. The radially outer end of the second suction path coincides with the radially outer end of the first suction path at the boundary between the cylinder and the head member. The compressor described. The second suction path is inclined in a direction parallel to the first suction path,
The first suction passage extends to an end face of the cylinder;
2. The radially outer end of the second suction path coincides with the radially outer end of the first suction path at the boundary between the cylinder and the head member. The compressor described.   A cutout portion having an inclined surface extending to the compression chamber while being inclined so as to be disposed radially inward as being away from the head member is provided at a corner portion on the inner peripheral side of the cylinder. The compressor according to any one of claims 1 to 3, wherein the compressor is provided.   5. The compressor according to claim 4, wherein, at a boundary between the cylinder and the head member, an end portion on the radially inner side of the second suction path is disposed on the radially outer side of the compression chamber.   An air conditioner using the compressor according to any one of claims 1 to 5.

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