CN115962127A - Rotary compressor and refrigeration cycle device - Google Patents

Abstract

The invention provides a rotary compressor and a refrigeration cycle device, which can improve the compression performance. The rotary compressor of the embodiment has a housing that houses a shaft and a compression mechanism inside. The compression mechanism includes an eccentric portion, a cylinder, a roller, a vane, a closing member, and an injection port. The cylinder has a cylinder chamber in which the eccentric portion is disposed. The roller is cylindrical, externally fitted to the eccentric portion, and eccentrically rotates in the cylinder chamber. The vane moves forward and backward along with the eccentric rotation of the roller, and divides the cylinder chamber into a suction chamber and a compression chamber for gas refrigerant. The closing member closes an end of the cylinder chamber in an axial direction of the shaft. The injection port is formed in the closing member, opens into the cylinder chamber, and injects the cooling refrigerant introduced from the outside of the housing into the cylinder chamber. The inlet is opened and closed by the end surfaces of the roller and the vane on the side of the closing member.

Description

Rotary compressor and refrigeration cycle device

Technical Field

Embodiments of the present invention relate to a rotary compressor and a refrigeration cycle device.

Background

In a refrigeration cycle apparatus, a rotary compressor that compresses a gas refrigerant is used. An injection circuit for injecting a cooling refrigerant into a cylinder chamber of a rotary compressor is proposed. For the rotary compressor, improvement of compression performance is required.

Patent document 1: japanese patent laid-open No. 2000-170678

Disclosure of Invention

The present invention addresses the problem of providing a rotary compressor and a refrigeration cycle device that can improve compression performance.

The rotary compressor of the embodiment has a housing that houses a shaft and a compression mechanism inside. The compression mechanism includes an eccentric portion, a cylinder, a roller, a vane, a closing member, and an injection port. The eccentric portion is provided to the shaft. The cylinder has a cylinder chamber in which the eccentric portion is disposed. The roller is cylindrical, is externally fitted to the eccentric portion, and eccentrically rotates in the cylinder chamber. The vane moves forward and backward along with the eccentric rotation of the roller, and divides the cylinder chamber into a suction chamber and a compression chamber of gas refrigerant. The closing member closes an end of the cylinder chamber in an axial direction of the shaft. The injection port is formed in the closing member, opens into the cylinder chamber, and injects the cooling refrigerant introduced from the outside of the housing into the cylinder chamber. The injection port is opened and closed by the end surfaces of the roller and the blade on the side of the closing member.

Drawings

Fig. 1 is a schematic configuration diagram of a refrigeration cycle apparatus including a cross-sectional view of a rotary compressor according to embodiment 1.

Fig. 2 is an explanatory diagram of an operation of the injection circuit of embodiment 1.

Fig. 3 is a graph showing a relationship between an eccentric rotation angle of the roller and an opening area ratio of the inlet.

Fig. 4 is a graph showing a relationship between the pressure of the cooling refrigerant injected into the circuit and the pressure of the compression chamber.

Fig. 5 is an explanatory diagram of the operation of the injection circuit of embodiment 2.

Fig. 6 is a partial sectional view of the rotary compressor of embodiment 3.

Fig. 7 is an explanatory diagram of the operation of the injection circuit of embodiment 3.

Description of the symbols

1: a refrigeration cycle device; 2: a rotary compressor; 3: a heat sink; 4: an expansion device; 5: a heat sink; 11: a housing; 13: a shaft; 14: a lubricating oil reservoir; 16: a partition member (closing member); 20: a compression mechanism section; 21: an eccentric portion; 22: a roller; 24: a cylinder body; 25: a cylinder chamber; 25p: a compression chamber; 25s: a suction chamber; 28: a suction hole; 28e: an end portion; 35, 37: an injection port; 40: a blade; 41: a blade receiving hole; 50: a blade; 51: a blade groove (blade receiving hole); 61: 1 st recess; 62: the 2 nd recess.

Detailed Description

Hereinafter, a rotary compressor and a refrigeration cycle apparatus according to an embodiment will be described with reference to the drawings.

Fig. 1 is a schematic configuration diagram of a refrigeration cycle apparatus including a cross-sectional view of the rotary compressor according to embodiment 1.

The refrigeration cycle apparatus 1 will be briefly described.

The refrigeration cycle apparatus 1 includes a rotary compressor 2, a radiator (e.g., a condenser) 3 connected to the rotary compressor 2, an expansion device (e.g., an expansion valve) 4 connected to the radiator 3, and a heat absorber (e.g., an evaporator) 5 connected between the expansion device 4 and the rotary compressor 2. The refrigeration cycle device 1 includes carbon dioxide (CO) ₂ ) And the like. The refrigerant circulates through the refrigerant flow path 8 of the refrigeration cycle apparatus 1 while changing phases.

The rotary compressor 2 compresses a low-pressure gas refrigerant (fluid) taken into the interior thereof to become a high-temperature high-pressure gas refrigerant. The specific structure of the rotary compressor 2 will be described later.

The radiator 3 radiates heat from the high-temperature high-pressure gas refrigerant supplied from the rotary compressor 2, and turns the high-temperature high-pressure gas refrigerant into a high-pressure liquid refrigerant.

The expansion device 4 reduces the pressure of the high-pressure liquid refrigerant sent from the radiator 3, and changes the high-pressure liquid refrigerant into a low-temperature low-pressure liquid refrigerant.

The heat absorber 5 vaporizes the low-temperature, low-pressure liquid refrigerant sent from the expansion device 4 into a low-pressure gas refrigerant. In the heat absorber 5, when the low-pressure liquid refrigerant is vaporized, vaporization heat is taken from the surroundings, and the surroundings are cooled. The low-pressure gas refrigerant having passed through the heat absorber 5 is taken into the rotary compressor 2.

As described above, in the refrigeration cycle apparatus 1 of the present embodiment, the refrigerant as the working fluid circulates through the refrigerant flow path 8 while changing the phase between the gas refrigerant and the liquid refrigerant. The refrigerant radiates heat during the phase change from the gas refrigerant to the liquid refrigerant, and absorbs heat during the phase change from the liquid refrigerant to the gas refrigerant. The heat dissipation and heat absorption are used to perform heating, cooling, and the like.

(embodiment 1)

A rotary compressor 2 according to embodiment 1 will be described. The rotary compressor 2 according to embodiment 1 is a so-called oscillating type rotary compressor 2 in which the vane 40 and the roller 22 are integrated.

In the present application, the Z direction (axial direction) is an axial direction of the central axis of the shaft 13. The + Z direction is a direction from the compression mechanism unit 20 toward the motor unit 15, and the-Z direction is the opposite side of the + Z direction. For example, the Z direction is a vertical direction, and the + Z direction is a vertically upward direction.

The rotary compressor 2 has an accumulator 6 and a compressor main body 10. The accumulator 6 separates the refrigerant sent from the heat absorber 5 into a gas refrigerant and a liquid refrigerant. The gas refrigerant is taken into the compressor body 10 through a suction pipe.

The compressor body 10 includes a casing 11, a shaft 13, a motor unit 15, a lubricant oil reservoir 14, a plurality of compression mechanism units 20, and an injection circuit 30.

The housing 11 is formed in a cylindrical shape with both ends closed. The housing 11 houses the shaft 13, the motor unit 15, the lubricant oil reservoir unit 14, and the plurality of compression mechanism units 20. The housing 11 has a supply portion 12 at an upper end thereof. The supply portion 12 supplies the gas refrigerant inside the housing 11 to the radiator 3.

The shaft 13 is disposed along the central axis of the compressor body 10. The shaft 13 has a plurality of eccentric portions 21.

The motor unit 15 is disposed in the + Z direction of the shaft 13. The motor unit 15 includes a stator 15a and a rotor 15b. The stator 15a is fixed to the inner circumferential surface of the housing 11. The rotor 15b is fixed to the outer peripheral surface of the shaft 13. The motor portion 15 rotates the drive shaft 13.

The lubricant oil reservoir 14 is an area inside the casing 11 and outside the plurality of compression mechanism units 20. The lubricant oil reservoir 14 stores lubricant oil for lubricating the sliding portion of the compressor main body 10. A lubricating oil flow path (not shown) is formed along the central axis from the lower end of the shaft 13. The lubricant oil in the lubricant oil reservoir 14 is supplied to the sliding portion of the compressor body 10 through the lubricant oil flow path with the rotation of the shaft 13.

The plurality of compression mechanism units 20 compress the gas refrigerant in accordance with the rotation of the shaft 13. The plurality of compression mechanism units 20 are arranged in the-Z direction of the shaft 13. The plurality of compression mechanism units 20 are fixed to the frame 11a. The outer peripheral surface of the frame 11a is fixed to the inner peripheral surface of the housing 11. The plurality of compression mechanisms 20 include two compression mechanisms 20, i.e., a 1 st compression mechanism 20A and a 2 nd compression mechanism 20B. The 1 st compression mechanism unit 20A and the 2 nd compression mechanism unit 20B are arranged in order from the + Z direction toward the-Z direction. The following describes the structure of the 1 st compression mechanism 20A as a representative example. The 2 nd compression mechanism unit 20B is the same as the 1 st compression mechanism unit 20A except for the eccentric direction of the eccentric portion 21.

The 1 st compression mechanism 20A includes an eccentric portion 21, a roller 22, a vane 40, and a cylinder 24.

The eccentric portion 21 has a cylindrical shape and is formed integrally with the shaft 13. The center of the eccentric portion 21 is eccentric from the center axis of the shaft 13 as viewed from the + Z direction.

The roller 22 is formed in a cylindrical shape and externally fitted to the outer periphery of the eccentric portion 21. The roller 22 eccentrically rotates together with the eccentric portion 21 inside the cylinder chamber 25.

Fig. 2 is a sectional view taken along line II-II of fig. 1.

As shown in fig. 2 (a), the blade 40 is formed integrally with the roller 22. The blade 40 has a flat plate shape. The vane 40 extends from the outer circumferential surface of the roller 22 toward the outer side in the radial direction of the roller 22. The cylinder 24 has a blade receiving hole 41. The pair of blade housing holes 41 are arranged in the radial direction of the shaft 13, and have a back pressure space 42a and a bushing groove 42b formed in a mutually connected state, and a throat portion 43 is formed between the back pressure space 42a and the bushing groove 42 b. A pair of substantially semicircular bushes 42c are fitted into the bush grooves 42 b. The pair of bushes 42c are configured to swing about the axial center of the bush groove 42 b. The back pressure space 42a is formed in a substantially circular shape. The vane 40 is housed between the pair of bushes 42c so as to be able to advance and retreat with the rotation of the roller 22.

In the present application, the X direction (1 st direction) and the Y direction (2 nd direction) are defined as follows. A line connecting the center of the shaft 13 and the center of the throat portion 43 (or the blade accommodating hole 41) in a plane perpendicular to the Z direction is taken as a reference line 44. The X direction is a direction parallel to the reference line 44. The + X direction is a direction from the center of the throat 43 toward the center of the shaft 13. The Y direction is a direction perpendicular to the Z direction and the X direction.

The cylinder 24 discharges the gas refrigerant compressed in the cylinder chamber 25 into the casing 11. The cylinder 24 has a cylinder chamber 25, a suction port 28, and a discharge port 29 (see fig. 1).

The cylinder chamber 25 is formed by penetrating the center of the cylinder 24 in the radial direction in the Z direction. The cylinder chamber 25 accommodates the eccentric portion 21, the roller 22, and the vane 40 therein. As shown in fig. 2 (d), the vane 40 partitions the interior of the cylinder chamber 25 into a suction chamber 25s and a compression chamber 25p together with the roller 22. The suction hole 28 communicates the suction chamber 25s with the accumulator 6 shown in fig. 1. The discharge port 29 is formed in the bearing 17 (the 1 st bearing 17A or the 2 nd bearing 17B). The discharge hole 29 communicates the compression chamber 25p with the muffler chamber 19 (1 st muffler chamber 19A or 2 nd muffler chamber 19B) via the spool 29 v.

By the eccentric rotation of the rollers 22, the volume of the suction chamber 25s increases. The gas refrigerant (refrigerant in state 1) is sucked from the accumulator 6 into the suction chamber 25s through the suction hole 28. By the eccentric rotation of the roller 22, the volume of the compression chamber 25p is reduced, and the gas refrigerant is compressed. If the gaseous refrigerant exceeds the discharge pressure, the valve spool 29v is pushed open. The gas refrigerant is discharged from the compression chamber 25p to the muffler chamber 19 through the discharge hole 29.

As shown in fig. 1, the rotary compressor 2 includes a partition member (closing member) 16, a 1 st bearing 17A, a 2 nd bearing 17B, a 1 st muffler 18A, and a 2 nd muffler 18B.

The partition member 16 is disposed between the 1 st compression mechanism 20A and the 2 nd compression mechanism 20B. The partition member 16 closes the end of the cylinder chamber 25 of the 1 st compression mechanism unit 20A in the-Z direction. The partition member 16 closes the end in the + Z direction of the cylinder chamber 25 of the 2 nd compression mechanism unit 20B.

The 1 st bearing (main bearing) 17A is disposed in the + Z direction of the plurality of compression mechanism units 20 and supports the shaft 13. The 1 st bearing 17A closes the end in the + Z direction of the cylinder chamber 25 of the 1 st compression mechanism unit 20A.

The 2 nd bearing (sub-bearing) 17B is disposed in the-Z direction of the plurality of compression mechanism sections 20 and supports the shaft 13. The 2 nd bearing 17B closes the end of the 2 nd compression mechanism unit 20B in the-Z direction of the cylinder chamber 25.

The 1 st muffler 18A forms a 1 st muffler chamber 19A with the 1 st bearing 17A. The gas refrigerant compressed by the 1 st compression mechanism 20A is discharged from the discharge port 29 to the 1 st muffler chamber 19A. The gas refrigerant discharged to the 1 st muffler chamber 19A is discharged to the inside of the housing 11 through the muffler hole 19 e.

The 2 nd muffler 18B forms a 2 nd muffler chamber 19B between the 2 nd bearing 17B. The gas refrigerant compressed by the 2 nd compression mechanism 20B is discharged from a discharge hole (not shown) to the 2 nd muffler chamber 19B. The 2 nd muffler chamber 19B communicates with the 1 st muffler chamber 19A via an inter-muffler-chamber passage (not shown).

The injection circuit 30 will be described in detail.

The injection circuit 30 intermittently injects the cooling refrigerant (the refrigerant in the 2 nd state, the intermediate-pressure refrigerant, and the liquid refrigerant) introduced from the outside of the casing 11 into the cylinder chamber 25. The injection circuit 30 includes a pipe 32, a relay valve 33, a branch flow path 34, and an injection port 35.

The pipe 32 introduces a cooling refrigerant from the outside of the casing 11. The pipe 32 branches from the refrigerant flow path 8 between the radiator 3 and the expansion device 4 of the refrigeration cycle apparatus 1. When the expansion device 4 includes a high-pressure-side expansion device and a low-pressure-side expansion device, the pipe 32 may be branched from the refrigerant passage 8 between the high-pressure-side expansion device and the low-pressure-side expansion device. The pipe 32 may be branched from the refrigerant flow path 8 via a gas-liquid separator. The pipe 32 extends through the case 11 and the lubricant oil reservoir 14 to the inside of the partition member 16. A gas-liquid two-phase refrigerant having a lower temperature than the gas refrigerant compressed by the compression mechanism 20 flows through the refrigerant passage 8 between the radiator 3 and the expansion device 4. The pipe 32 introduces the two-phase gas-liquid refrigerant into the casing 11 as a cooling refrigerant.

The relay valve 33 is provided in the pipe 32 outside the housing 11. The relay valve 33 can block the introduction of the cooling refrigerant into the casing 11.

The branch flow path 34 is formed in the partition member 16. The branch flow path 34 extends from the tip of the pipe 32 inside the partition member 16 toward the plurality of compression mechanism units 20. The branch flow path 34 communicates the injection ports 35 of the plurality of compression mechanism units 20 with the common pipe 32.

The inlet 35 is an opening of the branch flow path 34 to the cylinder chamber 25. The injection port 35 has a circular shape. The inlet 35 is formed in the partition member 16. The inlet 35 injects the cooling refrigerant introduced from the outside of the housing 11 into the cylinder chamber 25.

As shown in fig. 2 (d), the injection port 35 is disposed closer to the compression chamber 25p than the reference line 44 in the Y direction. The inlet 35 is disposed within the range of the width of the blade 40 disposed along the X direction in the Y direction. When the roller 22 is eccentrically rotated to the maximum extent in the + X direction, the injection port 35 is disposed between the outer periphery of the roller 22 and the outer periphery of the cylinder chamber 25 in the X direction. As shown in fig. 2 (a), when the roller 22 is eccentrically rotated to the maximum extent in the-X direction, the inlet 35 is disposed between the inner periphery and the outer periphery of the roller 22 in the X direction. The inlet 35 is not exposed to the inside of the inner periphery of the roller 22.

The effect of the injection circuit 30 is explained in comparison with the prior art. Fig. 2 is an explanatory diagram of the operation of the injection circuit 30, and is a sectional view taken along line II-II of fig. 1. In fig. 2, for comparison, a conventional injection port 35c is shown together with the injection port 35 of embodiment 1.

In the first half of the compression process of the gas refrigerant in the cylinder chamber 25 (see fig. 2 c), the pressure of the cooling refrigerant injected into the circuit 30 is higher than the pressure of the cylinder chamber 25. The cooling refrigerant is injected into the cylinder chamber 25 through the injection port. The liquid refrigerant contained in the injected cooling refrigerant absorbs heat in the cylinder chamber 25 and evaporates. Thereby, the gas refrigerant being compressed and the compression mechanism 20 are cooled. The amount of the compressed refrigerant increases and thus, the compression performance of the rotary compressor 2 is improved.

When the cooling refrigerant injected into the cylinder chamber 25 flows into the suction hole 28, the amount of gas refrigerant sucked into the cylinder chamber 25 from the suction hole 28 decreases. This reduces the compression performance of the rotary compressor 2. At the time of fig. 2 (b), the leading end of the roller 22 in the eccentric direction is located at the end 28e of the suction hole 28 on the downstream side in the eccentric rotation direction of the roller 22. When the injection port is opened to the cylinder chamber 25 before the time point of fig. 2 (b), the injected cooling refrigerant may flow into the suction port 28. It is required to close the injection port at least up to the time point (b) in fig. 2 (hereinafter, referred to as "1 st requirement").

As shown in fig. 1, the gas refrigerant compressed to the discharge pressure in the cylinder chamber 25 is discharged to the inside of the housing 11. The pressure of the lubricating oil reservoir 14 housed inside the housing 11 is the same as the discharge pressure. As described above, the lubricant oil in the lubricant oil reservoir 14 is supplied to the sliding portion of the compressor body 10 through the lubricant oil flow path formed along the center axis of the shaft 13. Inside the inner circumference of the roller 22, there is lubricating oil at discharge pressure. If the injection port is opened inward of the inner periphery of the roller 22, there is a possibility that the lubricating oil flows into the injection circuit 30 from the injection port. The injection port is required not to open to the inner side of the inner periphery of the roller 22 (hereinafter, referred to as requirement 2).

Fig. 4 is a graph showing a relationship between the pressure of the cooling refrigerant in the injection circuit 30 and the pressure of the compression chamber 25p. The horizontal axis in fig. 4 represents an eccentric rotation angle (may be simply referred to as a rotation angle) θ of the roller 22 from the reference line 44. The rotation angle θ is an angle from the center of the throat 43 to the front end of the eccentric direction of the roller 22 in the eccentric rotation direction of the roller 22. In fig. 4, the solid line indicates the pressure of the compression chamber 25p at the time of high load, and the broken line indicates the pressure of the compression chamber 25p at the time of low load. The one-dot chain line indicates the pressure of the cooling refrigerant in the injection circuit 30 at the time of high load, and the two-dot chain line indicates the pressure of the cooling refrigerant in the injection circuit 30 at the time of low load. The high load state is a state where the rotary compressor 2 is operated at a high rotation speed, and the low load state is a state where the rotary compressor 2 is operated at a low rotation speed. At a high load, the pressure of the refrigerant flowing through the refrigeration cycle apparatus 1 becomes high. Accordingly, the pressure of the cooling refrigerant in the injection circuit 30 becomes high. Further, the pressure inside the casing 11 increases, and the discharge pressure of the gas refrigerant from the compression chamber 25p increases.

The pressure of the compression chamber 25p increases with the increase in the rotation angle θ. At the time of high load, at the time of θ =180 °, the pressure of the compression chamber 25p is higher than the pressure of the cooling refrigerant of the injection circuit 30. After the time θ =180 °, if the injection port is opened to the compression chamber 25p, the compressed gas refrigerant may flow into the injection circuit 30 from the injection port. It is required that the injection port be closed at least after the time of θ =180 ° (hereinafter, referred to as a 3 rd requirement).

The inlet 35c of the conventional technique is opened and closed only by the end surface of the roller 22 in the Z direction. Therefore, the degree of freedom in design regarding the position and the opening area of the injection port 35c is small. As shown in fig. 2 (a), the injection port 35c is located at a position where the rotation angle θ is about 315 °. The injection port 35c opens to the cylinder chamber 25 at the time point (b) of fig. 2. The inlet 35c is closest to the inner periphery of the roller 22 at the time (f) in fig. 2, but is not opened just inward of the inner periphery. The degree of freedom in designing the inlet 35c is small, and there is a limit in designing the inlet so as to satisfy the 1 st and 2 nd requirements.

Fig. 3 is a graph showing a relationship between an eccentric rotation angle of the roller and an opening area ratio of the injection port. In the graph of fig. 3, the solid line indicates the inlet 35 of the embodiment, and the broken line indicates the inlet 35c of the related art. The opening area of the inlet on the vertical axis is normalized with the maximum opening area of the conventional inlet 35c set to 1.

The degree of freedom in designing the inlet 35c of the related art is small. The range of the rotation angle θ at which the injection port 35c is opened with the maximum opening area is increased. The injection port 35c opens into the compression chamber 25p at the time θ =180 ° in fig. 2 (d). As shown in fig. 3, the injection port 35c is not closed until the rotation angle θ becomes about 225 °. The injection port 35c cannot satisfy the requirement of the 3 rd.

The degree of freedom in designing the inlet 35c of the related art is small. It is difficult to increase the opening area of the inlet 35c. The cooling refrigerant injected into the cylinder chamber 25 is insufficient. The improvement of the cooling performance and the compression performance of the rotary compressor 2 is limited.

The inlet 35 of the embodiment is opened and closed by the Z-direction end surfaces of the roller 22 and the blade 40. Therefore, the degree of freedom in design regarding the position and the opening area of the inlet 35 is large. Since the swing blade 40 opens and closes the inlet 35, the inlet 35 can be designed with a great degree of freedom. As shown in fig. 2 (a), the injection port 35 is located immediately before the rotation angle θ becomes 360 °.

Fig. 2 (a) shows the time at which θ =0 °. The inlet 35 is closed by the Z-direction end surface of the roller 22. The inlet 35 is closest to the inner periphery of the roller 22, but does not open inward of the inner periphery. The injection port 35 satisfies the requirement of 2 nd. The lubricant oil on the inner side of the inner periphery of the roller 22 is less likely to flow into the inlet 35. The shortage of the lubricating oil in the rotary compressor 2 can be suppressed.

In fig. 2 (b), the leading end in the eccentric direction of the roller 22 is located at the end 28e of the suction hole 28 on the downstream side in the eccentric rotation direction of the roller 22. The rotation angle θ in fig. 2 (b) is θ 1. The inlet 35 is closed by the Z-direction end surface of the roller 22. The injection port 35 satisfies the 1 st requirement.

Fig. 2 (c) is a time at which θ =90 °. The entire injection port 35 opens into the cylinder chamber 25. The injection port 35 is opened only by the end surface of the roller 22 in the Z direction. The inlet 35 moves relatively in the radial direction of the roller 22, and is shifted from a fully closed state in which the entire structure is closed to a fully open state in which the opening area is maximized. As shown in fig. 3, the opening of the injection port 35 is performed in a short time within a narrow range of the rotation angle θ.

Fig. 2 (d) is a time at which θ =180 °. The entire inlet 35 is closed by the Z-direction end surface of the blade 40. In fig. 2 (e) and 2 (f) of 180 ° < θ, the inlet 35 is also closed by the Z-direction end face of the blade 40 or the roller 22. The injection port 35 satisfies the requirement of the 3 rd. At high load, the gas refrigerant compressed in the cylinder chamber 25 is less likely to flow into the injection circuit 30 through the injection port 35.

As shown in fig. 4, at the time when the rotation angle θ is 140 ° at the time of low load, the pressure of the compression chamber 25p is higher than the pressure of the cooling refrigerant in the injection circuit 30. As shown in fig. 3, when θ =140 °, the opening area ratio of the injection port 35 of the embodiment is the same as that of the injection port 35c of the related art. At 140 ° < θ, the opening area ratio of the inlet 35 of the embodiment is smaller than that of the inlet 35c of the related art. Even at a low load, the gas refrigerant compressed in the cylinder chamber 25 is less likely to flow into the injection circuit 30 from the injection port 35.

The injection port 35 of the embodiment has a large degree of freedom in design. The opening area of the injection port 35 can be increased. As shown in fig. 3, the opening area of the injection port 35 of the embodiment is 2 times as large as that of the injection port 35c of the related art. The pressure loss of the cooling refrigerant at the inlet 35 can be suppressed. A sufficient amount of cooling refrigerant can be injected into the cylinder chamber 25. The cooling performance and the compression performance of the rotary compressor 2 are improved.

As shown in fig. 2 (b), an angle from the center of the throat 43 (or the vane housing hole 41) to the end 28e of the suction hole 28 in the eccentric rotation direction of the roller 22 is θ 1. As shown in fig. 2 (c), the angle from the center of the throat 43 (or the blade accommodating hole 41) to the tip in the eccentric direction of the roller 22 having the largest opening area of the inlet 35 is θ max. At this time, the following equation 1 holds.

θ1<θmax<140°……(1)

As shown in fig. 3, θ 1 is about 30 °. θ max is approximately 90 ° < θ max <110 °. θ max satisfies mathematical formula 1.

With θ 1< θ max, the opening area of the inlet 35 is maximized after the leading end of the roller 22 in the eccentric direction passes the end 28e of the suction hole 28. Since the opening area of the injection port 35 is not maximized, the inflow of the cooling refrigerant into the suction hole 28 can be suppressed.

When θ max <140 °, the opening area of the injection port 35 is maximized before the pressure of the compression chamber 25p becomes higher than the pressure of the cooling refrigerant in the injection circuit 30 at the time of low load. Since the opening area of the injection port 35 does not become the maximum after that, the inflow of the compressed gas refrigerant into the injection port 35 can be suppressed.

As described above in detail, in the rotary compressor 2 according to embodiment 1, the inlet 35 of the cooling refrigerant is opened and closed by the end surfaces of the roller 22 and the vane 40 on the partition member 16 side.

The degree of freedom in designing the inlet 35 is large. After the pressure of the gas refrigerant in the cylinder chamber 25 is higher than the pressure of the cooling refrigerant, the injection port 35 is not opened to the cylinder chamber 25. The gas refrigerant is difficult to flow into the injection port 35. The compression performance of the rotary compressor 2 is improved.

The vanes 40 are integral with the roller 22.

Since the swing blade 40 opens and closes the inlet 35, the inlet 35 can be designed with a great degree of freedom. The compression performance of the rotary compressor 2 is improved.

Since no gap is formed between the vane 40 and the outer peripheral surface of the roller 22, the inlet 35 can be closed without a gap.

The transition from the closed state to the state in which the opening area is the largest is performed only by the end surface of the roller 22 on the partition member 16 side.

When the injection port 35 is opened, the pressure of the cooling refrigerant is significantly higher than the pressure of the cylinder chamber 25. The opening of the inlet 35 is performed only by the end surface of the roller 22 on the side of the partition member 16 in a short time. The pressure loss of the cooling refrigerant can be suppressed, and a sufficient amount of the cooling refrigerant can be injected into the cylinder chamber 25. The cooling performance and the compression performance of the rotary compressor 2 are improved.

An angle from the center of the throat 43 (or the vane housing hole 41) to the end 28e of the suction hole 28 on the downstream side in the eccentric rotation direction of the roller 22 is θ 1. In the eccentric rotation direction of the roller 22, an angle from the center of the throat portion 43 (or the blade accommodating hole 41) to the tip end of the roller 22 in the eccentric direction where the opening area of the inlet 35 is maximized is defined as θ max. At this time, θ 1< θ max <140 ° holds.

The cooling refrigerant can be prevented from flowing into the suction hole 28 by θ 1< θ max. By θ max <140 °, the inflow of the compressed gas refrigerant into the inlet 35 can be suppressed. The compression performance of the rotary compressor 2 is improved.

The refrigeration cycle apparatus 1 according to embodiment 1 includes the rotary compressor 2, the radiator 3, the expansion device 4, and the heat absorber 5 described above. The radiator 3 is connected to the rotary compressor 2. The expansion device 4 is connected to the radiator 3. The heat absorber 5 is connected between the expansion device 4 and the rotary compressor 2.

Since the rotary compressor 2 is provided, the performance of the refrigeration cycle apparatus 1 can be improved.

(embodiment 2)

The rotary compressor according to embodiment 2 will be described.

Fig. 5 is a sectional view of a portion corresponding to line II-II of fig. 1. The rotary compressor of embodiment 2 is different from embodiment 1 of the swing type in that it is a rotary type. Description of the portion of embodiment 2 having the same configuration as embodiment 1 is omitted.

The rotary compressor according to embodiment 2 is a so-called rotary compressor in which the vane 50 and the roller 22 are separate bodies.

As shown in fig. 5 (c), the blade 50 has a flat plate shape. The cylinder 24 has a vane groove 51 as a vane housing hole, and supports the vane 50 to be able to advance and retreat in the cylinder chamber 25. The vane 50 is disposed inside the vane groove 51. The vane 50 is movable in the X direction along the vane groove 51. A lubricating oil hole 52 is formed at the-X direction end of the vane groove 51. The lubricating oil in the lubricating oil reservoir portion 14 is introduced into the lubricating oil hole 52. As described above, the lubricating oil is at the discharge pressure. The vane 50 is biased in the + X direction by the lubricating oil in the lubricating oil hole 52. The tip of the vane 50 in the + X direction abuts on the outer peripheral surface of the roller 22. The vane 50 moves in and out of the vane groove 51 relative to the cylinder chamber 25 in accordance with the eccentric rotation of the roller 22.

The injection circuit has an injection port 37.

The injection port 37 has an oblong or elliptical shape. The length of the injection port 37 in the X direction is longer than the length in the Y direction. The injection port 37 is formed in a sliding region of the partition member 16 with respect to the blade 50. The injection port 37 is disposed closer to the compression chamber 25p of the cylinder chamber 25 than the center of the sliding region in the Y direction. The injection port 37 is disposed on the compression chamber 25p side of the reference line 44 in the Y direction.

As shown in fig. 5 (a), when the roller 22 is eccentrically rotated to the maximum extent in the-X direction, the inlet 37 is disposed between the inner periphery and the outer periphery of the roller 22 in the X direction. As shown in fig. 5 (c), when the roller 22 is eccentrically rotated to the maximum extent in the + X direction, the injection port 37 is disposed between the outer periphery of the roller 22 and the outer periphery of the cylinder chamber 25 in the X direction. As described below, the injection port 37 opens into the cylinder chamber 25 between the tip of the vane 50 and the outer peripheral surface of the roller 22.

The function of the injection circuit will be explained.

Fig. 5 is an explanatory diagram of the operation of the injection circuit, and is a sectional view of a portion corresponding to line II-II in fig. 1. The inlet 37 is opened and closed by the Z-direction end surfaces of the roller 22 and the vane 50. Therefore, the degree of freedom in designing the inlet 37 is large.

Fig. 5 (a) shows the time at which θ =0 °. The inlet 37 is closed by the Z-direction end surface of the roller 22. The inlet 37 is closest to the inner periphery of the roller 22, but is not open to the inner side of the inner periphery. The injection port 37 satisfies the requirement 2. The lubricant oil on the inner side of the inner periphery of the roller 22 is less likely to flow into the inlet 37. The shortage of the lubricating oil in the rotary compressor can be suppressed.

At a time between fig. 5 (a) and fig. 5 (b), the eccentric-direction leading ends of the rollers 22 pass through the end 28e of the suction hole 28. The inlet 37 is closed by the Z-direction end surface of the roller 22 until that time. The injection port 37 satisfies the 1 st requirement.

Fig. 5 (b) shows the timing θ =90 °, which is the first half of the compression process of the cylinder chamber 25. The inlet 37 opens into the cylinder chamber 25 between the tip of the vane 50 and the outer peripheral surface of the roller 22. The roller 22 eccentrically rotates toward the suction chamber 25s side of the reference line 44. The clearance between the tip of the vane 50 and the outer peripheral surface of the roller 22 is larger on the compression chamber 25p side than on the suction chamber 25s side of the reference line 44. The injection port 37 is disposed on the compression chamber 25p side of the reference line 44 in the Y direction. The opening area of the inlet 37 to the cylinder chamber 25 is increased. A sufficient amount of cooling refrigerant is injected into the cylinder chamber 25 through the injection port 37.

Fig. 5 (c) shows the time θ =180 °, which is the latter half of the compression process of the cylinder chamber 25. The entire inlet 37 is closed by the Z-direction end surface of the vane 50.

Fig. 5 (d) shows a time at which θ =270 °. The roller 22 eccentrically rotates toward the compression chamber 25p side of the reference line 44. The clearance between the tip of the vane 50 and the outer peripheral surface of the roller 22 is smaller on the compression chamber 25p side than on the suction chamber 25s side of the reference line 44. The injection port 37 is disposed on the compression chamber 25p side of the reference line 44 in the Y direction. Between the tip of the vane 50 and the outer peripheral surface of the roller 22, the opening area of the inlet 37 to the cylinder chamber 25 is reduced. The inflow of the gas refrigerant compressed inside the cylinder chamber 25 into the injection circuit from the injection port 17 is reduced. In the range of 180 ° < θ, the injection port 37 is almost closed. The injection port 37 satisfies the 3 rd requirement. At high load, the gas refrigerant compressed in the cylinder chamber 25 is less likely to flow into the injection circuit through the injection port 37.

In the same manner as in embodiment 1, the angle from the center of the vane groove 51 to the end 28e of the suction hole 28 in the eccentric rotation direction of the roller 22 is θ 1. The angle from the center of the vane groove 51 to the end of the roller 22 in the eccentric direction where the opening area of the inlet 37 is maximized is represented by θ max. At this time, θ 1< θ max <140 ° holds.

As described above in detail, in the rotary compressor according to embodiment 2 shown in fig. 5 (c), the vane 50 is separate from the roller 22. The inlet 37 is formed in a region of the partition member 16 that slides against the vane 50, at a position closer to the compression chamber 25p than the center in the Y direction. The inlet 37 opens into the cylinder chamber 25 between the tip of the vane 50 on the cylinder chamber 25 side and the outer peripheral surface of the roller 22.

The degree of freedom in designing the inlet 37 is large. In the first half of the compression process, the opening area of the injection port 37 is increased, and a sufficient amount of the cooling refrigerant is injected into the cylinder chamber 25. In the latter half of the compression process, the opening area of the injection port 37 is reduced, and the compressed gas refrigerant is less likely to flow into the injection circuit 30 from the injection port 37. The compression performance of the rotary compressor is improved.

The length of the injection port 37 in the X direction is longer than the length in the Y direction.

By adjusting the length of the injection port 37 in the X direction, the range of the rotation angle θ of the injection port 37 opening to the cylinder chamber 25 can be adjusted. A sufficient amount of cooling refrigerant is injected into the cylinder chamber 25.

(embodiment 3)

The rotary compressor according to embodiment 3 will be described.

Fig. 6 is a partial sectional view of the rotary compressor of embodiment 3. Fig. 7 is a sectional view taken along line VII-VII of fig. 6. The 1 st compression mechanism 20A in fig. 6 is in the state of fig. 7 (B), and the 2 nd compression mechanism 20B is in the state of fig. 7 (d).

As shown in fig. 7, the rotary compressor of embodiment 3 is of the same rotary type as embodiment 2. As shown in fig. 6, embodiment 3 differs from embodiment 2 in that the inlet 37 is an opening of the 1 st recess 61, in that the inlet 37 is an opening of a branch channel. Description of the same components as those of embodiment 2 will be omitted in embodiment 3.

The injection circuit includes an injection port 37, a 1 st recess 61, a 2 nd recess 62, a 3 rd recess 63, a distribution channel 64, and a pipe 32. Hereinafter, the injection port 37, the 1 st concave portion 61, the 2 nd concave portion 62, and the 3 rd concave portion 63 formed on the 1 st compression mechanism portion 20A side will be described, but these members are similarly formed on the 2 nd compression mechanism portion 20B side.

The inlet 37 is an opening of the 1 st recess 61.

The 1 st recess 61 is formed in the end surface of the partition member 16 on the 1 st compression mechanism portion 20A side.

The 2 nd recess 62 is formed in the end surface of the blade 50 on the partition member 16 side. The opening of the 2 nd recess 62 is closed by the partition member 16. The 2 nd recessed portion 62 extends in the X direction from the center portion of the blade 50 in the X direction toward the end portion in the + X direction. The end of the 2 nd recess 62 in the + X direction can communicate with the 1 st recess 61.

The 3 rd recess 63 is formed in the end surface of the partition member 16 on the 1 st compression mechanism portion 20A side. The opening of the 3 rd recess 63 is closed by the cylinder 24 of the 1 st compression mechanism section 20A. As shown in fig. 7 (b), the 3 rd concave portion 63 extends along the Y direction. The end of the 3 rd recess 63 opens into the vane groove 51 formed in the cylinder 24.

The pipe 32 extends from the outside to the inside of the housing 11. The pipe 32 is disposed in the cylinder 24 of the 1 st compression mechanism section 20A.

As shown in fig. 6, the distribution flow path 64 extends in the-Z direction from the distal end of the pipe 32. The distribution flow path 64 communicates with the 3 rd concave portion 63 formed on the 1 st compression mechanism section 20A side of the partition member 16. The distribution flow channel 64 penetrates the partition member 16 in the Z direction. The distribution flow path 64 communicates with the 3 rd concave portion 63 formed on the 2 nd compression mechanism section 20B side of the partition member 16.

The function of the injection circuit will be explained.

Fig. 7 is an explanatory diagram of the operation of the injection circuit, and is a sectional view taken along line VII-VII of fig. 6.

Fig. 7 (a) shows the time at which θ =0 °. The vane 50 moves maximally in the-X direction. The end of the 2 nd recess 62 in the + X direction does not communicate with the 1 st recess 61. The inlet 37 is closed by the Z-direction end surface of the roller 22. The cooling refrigerant is not injected into the cylinder chamber 25 through the injection port 37.

Fig. 7 (b) shows the time at which θ =90 °. The blade 50 moves in the + X direction. The end of the 2 nd recess 62 in the-X direction communicates with the 3 rd recess 63, and the end of the + X direction communicates with the 1 st recess 61. The pipe 32, the distribution channel 64, the 3 rd concave portion 63, the 2 nd concave portion 62, the 1 st concave portion 61, and the injection port 37 are sequentially communicated. The inlet 37 opens into the cylinder chamber 25 between the tip of the vane 50 and the outer peripheral surface of the roller 22. A cooling refrigerant is injected into the cylinder chamber 25 through the injection port 37.

Fig. 7 (c) shows the time at which θ =180 °. The vane 50 moves maximally in the + X direction. The end of the 2 nd recess 62 in the-X direction does not communicate with the 3 rd recess 63. The inlet 37 is closed by the Z-direction end surface of the blade 50. The cooling refrigerant is not injected into the cylinder chamber 25 through the injection port 37.

Fig. 7 (d) shows the time at which θ =270 °. The blade 50 moves in the-X direction. the-X direction end of the 2 nd recess 62 communicates with the 3 rd recess 63, and the + X direction end communicates with the 1 st recess 61. As in embodiment 2, the opening area of the inlet 37 to the cylinder chamber 25 is small between the tip of the vane 50 and the outer peripheral surface of the roller 22. The inflow of the compressed gas refrigerant into the injection circuit from the injection port 17 is reduced.

In embodiment 3 as well, as in embodiment 2, a cooling refrigerant is intermittently injected from the injection port 37 into the cylinder chamber 25.

As described above in detail, in the rotary compressor according to embodiment 3 shown in fig. 6, the injection port 37 is an opening formed in the 1 st recess 61 of the partition member 16. The blade 50 has a 2 nd recess 62 capable of communicating with the 1 st recess 61 on the end surface on the partition member 16 side.

The pipe 32 for injecting the cooling refrigerant into the circuit can be disposed in the cylinder 24, not in the partition member 16. In addition to the bearing 17, a discharge hole 29 of the cylinder chamber 25 may be formed in the partition member 16. The compression performance of the rotary compressor is improved.

In the above embodiment, the rotary compressor 2 includes two compression mechanisms 20 (the 1 st compression mechanism 20A and the 2 nd compression mechanism 20B). In contrast, the rotary compressor 2 may have only 1 compression mechanism unit 20, or may have 3 or more compression mechanism units 20.

In the above-described embodiment, the rotary compressor that cools the compression mechanism unit by injecting the liquid refrigerant has been described, but a rotary compressor that injects a gas refrigerant at an intermediate pressure may be used. This makes it possible to provide a rotary compressor that can improve energy saving and increase cooling and heating capacity while suppressing a decrease in reliability.

According to at least one embodiment described above, the injection ports 35 and 37 are opened and closed by the end surfaces of the roller 22 and the blades 40 and 50 on the side of the partition member 16. This can improve the compression performance of the rotary compressor.

The present invention is not limited to the refrigeration cycle apparatus 1 using the rotary compressor 2 of the present embodiment. In the rotary compressor 2 of the above embodiment, a configuration using two cylinders has been described, but the present invention is not limited to this. The number of cylinders may be 1, or 3 or more.

The 1 st bearing 17A or the 2 nd bearing 17B may be a sealing member, and the injection ports 35 and 37 may be provided in the 1 st bearing 17A or the 2 nd bearing 17B.

Several embodiments of the present invention have been described, but these embodiments are presented as examples and are not intended to limit the scope of the invention. These embodiments can be implemented in other various ways, and various omissions, substitutions, and changes can be made without departing from the spirit of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the inventions described in the claims and the equivalent scope thereof.

Claims (8)

1. A rotary compressor, wherein,

a housing for accommodating the shaft and the compression mechanism therein,

the compression mechanism includes:

an eccentric portion provided to the shaft;

a cylinder having a cylinder chamber in which the eccentric portion is disposed;

a roller which is cylindrical, is externally fitted to the eccentric portion, and eccentrically rotates in the cylinder chamber;

a vane which moves forward and backward along with the eccentric rotation of the roller and divides the cylinder chamber into a suction chamber and a compression chamber of the refrigerant in the 1 st state;

a closing member that closes an end portion of the cylinder chamber in an axial direction of the shaft; and

an injection port formed in the closing member and opening to the cylinder chamber, for injecting the refrigerant in the 2 nd state introduced from the outside of the casing into the cylinder chamber,

the inlet is opened and closed by the end surfaces of the roller and the vane on the side of the closing member.

2. The rotary compressor of claim 1,

the vane is integral with the roller.

3. The rotary compressor of claim 1 or 2,

the transition from the closed state to the state in which the opening area is maximized is performed only by the end surface of the roller on the closing member side.

4. The rotary compressor of claim 1,

the vane is separated from the roller and is movable in a 1 st direction along a vane groove formed in the cylinder, a leading end of the 1 st direction on the cylinder chamber side abuts on an outer peripheral surface of the roller,

the injection port is formed in a region of the closing member that slides with respect to the vane, at a position closer to the compression chamber than a center in a 2 nd direction orthogonal to the axial direction and the 1 st direction,

the injection port opens into the cylinder chamber between a tip of the vane on the cylinder chamber side and an outer peripheral surface of the roller.

5. The rotary compressor of claim 4,

the length of the injection port in the 1 st direction is longer than the length of the injection port in the 2 nd direction.

6. The rotary compressor of claim 4 or 5,

the injection port is an opening formed in the 1 st recess of the closing member,

the blade has a 2 nd recess portion that can communicate with the 1 st recess portion on the end surface on the closing member side.

7. The rotary compressor of any one of claims 1 to 6,

the vane moves in and out of the cylinder chamber from a vane housing hole formed in the cylinder in accordance with the eccentric rotation of the roller,

the cylinder has a suction hole for sucking the refrigerant in the 1 st state into the cylinder chamber,

when the angle from the center of the blade accommodating hole to the end of the suction hole on the downstream side of the eccentric rotation direction of the roller is set as theta 1 in the eccentric rotation direction of the roller,

when an angle from the center of the blade accommodating hole to the tip of the roller in the eccentric direction where the opening area of the inlet is maximized in the eccentric rotation direction of the roller is defined as θ max,

θ 1< θ max <140 ° holds.

8. A refrigeration cycle apparatus includes:

the rotary compressor of any one of claims 1 to 7;

a radiator connected to the rotary compressor;

an expansion device connected to the radiator; and

and a heat absorber connected between the expansion device and the rotary compressor.

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