CN115962127A - Rotary compressor and refrigeration cycle device - Google Patents

Abstract

The invention provides a rotary compressor and a refrigeration cycle device capable of improving compression performance. The rotary compressor of the embodiment has a casing that houses a shaft and a compression mechanism therein. The compression mechanism part has an eccentric part, 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 arranged. The roller is cylindrical, embedded in the eccentric part, and rotates eccentrically in the cylinder chamber. The vane moves forward and backward 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 the end of the cylinder chamber in the axial direction of the shaft. The injection port is formed in the closing member, opens to the cylinder chamber, and injects the cooling refrigerant introduced from the outside of the casing into the cylinder chamber. The injection port is opened and closed by the roller and the end surface of the vane on the closing member side.

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 technique

In a refrigeration cycle device, a rotary compressor that compresses a gaseous refrigerant is used. An injection circuit for injecting cooling refrigerant into a cylinder chamber of a rotary compressor has been proposed. For rotary compressors, improved compression performance is required.

Patent Document 1: Japanese Patent Laid-Open No. 2000-170678

Contents of the invention

The problem to be solved by the present invention is to provide a rotary compressor and a refrigeration cycle device capable of improving compression performance.

The rotary compressor of the embodiment has a casing that houses a shaft and a compression mechanism therein. The compression mechanism part has an eccentric part, a cylinder, a roller, a vane, a closing member, and an injection port. The eccentric portion is provided on the shaft. The cylinder has a cylinder chamber in which the eccentric portion is arranged. The roller is cylindrical, embedded in the eccentric part, and rotates eccentrically in the cylinder chamber. The vane moves forward and backward 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 the end of the cylinder chamber in the axial direction of the shaft. The injection port is formed in the closing member, opens to the cylinder chamber, and injects the cooling refrigerant introduced from the outside of the casing into the cylinder chamber. The injection port is opened and closed by the roller and the end surface of the vane on the closing member side.

Description of drawings

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

Fig. 2 is an explanatory diagram of the operation of the injection circuit according to the first embodiment.

3 is a graph showing the relationship between the eccentric rotation angle of the roller and the opening area ratio of the injection port.

Fig. 4 is a graph showing the 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 the second embodiment.

Fig. 6 is a partial sectional view of a rotary compressor according to a third embodiment.

Fig. 7 is an explanatory diagram of the operation of the injection circuit according to the third embodiment.

Explanation of symbols

1: Refrigeration cycle device; 2: Rotary compressor; 3: Radiator; 4: Expansion device; 5: Heat absorber; 11: Shell; 13: Shaft; 14: Lubricating oil storage; 16: Partition ( closing part); 20: compression mechanism; 21: eccentric; 22: roller; 24: cylinder; 25: cylinder chamber; 25p: compression chamber; 25s: suction chamber; 28: suction hole; 28e: end ; 35, 37: injection port; 40: blade; 41: blade receiving hole; 50: blade; 51: blade groove (blade receiving hole); 61: first concave portion; 62: second concave portion.

Detailed ways

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

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

The refrigeration cycle device 1 will be briefly described.

The refrigeration cycle device 1 has a rotary compressor 2, a radiator (such as a condenser) 3 connected to the rotary compressor 2, an expansion device (such as an expansion valve) 4 connected to the radiator 3, and an expansion device (such as an expansion valve) 4 connected to the Heat absorber (eg evaporator) 5 between rotary compressors 2 . The refrigeration cycle device 1 contains a refrigerant such as carbon dioxide (CO ₂ ). The refrigerant circulates in the refrigerant flow channel 8 of the refrigeration cycle device 1 while changing phases.

The rotary compressor 2 compresses the low-pressure gas refrigerant (fluid) taken inside to become a high-temperature, high-pressure gas refrigerant. The specific configuration 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, so that the high-pressure liquid refrigerant becomes a low-temperature and low-pressure liquid refrigerant.

The heat absorber 5 vaporizes the low-temperature and 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 vaporizes, the heat of vaporization is taken from the surroundings, thereby cooling the surroundings. The low-pressure gas refrigerant having passed through the heat absorber 5 is taken into the interior of the rotary compressor 2 described above.

Thus, in the refrigeration cycle apparatus 1 of this embodiment, the refrigerant|coolant which is a working fluid circulates in the refrigerant flow path 8 while changing phases between gas refrigerant and liquid refrigerant. The refrigerant dissipates heat during the phase change from gas refrigerant to liquid refrigerant, and absorbs heat during the phase change from liquid refrigerant to gas refrigerant. Use these heat dissipation and heat absorption to perform heating, cooling, and the like.

(first embodiment)

The rotary compressor 2 of the first embodiment will be described. The rotary compressor 2 of the first embodiment is a so-called swing type rotary compressor 2 in which the vanes 40 and the rollers 22 are integrated.

In the present application, the Z direction (axial direction) is the 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 to the +Z direction. For example, the Z direction is the vertical direction, and the +Z direction is the vertical 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. Gas refrigerant is taken into the compressor main body 10 through a suction pipe.

The compressor main body 10 has a casing 11 , a shaft 13 , a motor unit 15 , a lubricating oil storage unit 14 , a plurality of compression mechanism units 20 , and an injection circuit 30 .

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

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

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

The lubricating oil storage portion 14 is an area inside the casing 11 and outside the plurality of compression mechanism portions 20 . The lubricating oil storage portion 14 stores lubricating 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 portion of the shaft 13 . The lubricating oil in the lubricating oil storage portion 14 is supplied to the sliding portion of the compressor main body 10 through the lubricating oil passage along with the rotation of the shaft 13 .

The plurality of compression mechanism units 20 compress the gas refrigerant as the shaft 13 rotates. The plurality of compression mechanism units 20 are arranged in the −Z direction of the shaft 13 . The plurality of compression mechanism parts 20 are fixed to the frame 11a. The outer peripheral surface of the frame 11 a is fixed to the inner peripheral surface of the housing 11 . The plurality of compression mechanism units 20 includes two compression mechanism units 20 of a first compression mechanism unit 20A and a second compression mechanism unit 20B. 20 A of 1st compression mechanism parts and 20 B of 2nd compression mechanism parts are arrange|positioned in order from +Z direction toward -Z direction. Hereinafter, the configuration of the first compression mechanism unit 20A will be described as a representative one. The configuration of the second compression mechanism part 20B is the same as that of the first compression mechanism part 20A except for the eccentric direction of the eccentric part 21 .

20 A of 1st compression mechanism parts have the eccentric part 21, the roller 22, the vane 40, and the cylinder 24.

The eccentric portion 21 is cylindrical and integrally formed with the shaft 13 . The center of the eccentric portion 21 is eccentric from the central axis of the shaft 13 when viewed from the +Z direction.

The roller 22 is formed in a cylindrical shape and is fitted on the outer periphery of the eccentric portion 21 . The roller 22 rotates eccentrically 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 (a) of FIG. 2 , the blade 40 is integrally formed with the roller 22 . The blade 40 has a flat plate shape. The vane 40 extends from the outer peripheral surface of the roller 22 toward the radially outer side of the roller 22 . The cylinder body 24 has a vane storage hole 41 . The pair of vane receiving holes 41 are arranged in the radial direction of the shaft 13 , have a back pressure space 42 a and a bushing groove 42 b connected to each other, and a throat 43 is formed between the back pressure space 42 a and the bushing groove 42 b. A pair of substantially semicircular bushes 42c are fitted into the bush grooves 42b. The pair of bushes 42c are configured to swing about the axis of the bush groove 42b. 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 as the roller 22 rotates.

In the present application, the X direction (first direction) and the Y direction (second direction) are defined as follows. In a plane perpendicular to the Z direction, a line connecting the center of the connecting shaft 13 and the center of the throat 43 (or the vane housing hole 41 ) is defined 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 hole 28, and a discharge hole 29 (see FIG. 1 ).

The cylinder chamber 25 is formed by penetrating the radial center of the cylinder 24 along the Z direction. The cylinder chamber 25 accommodates the eccentric part 21, the roller 22, and the vane 40 inside. As shown in FIG. 2( d ), the vane 40 partitions the inside 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 hole 29 is formed in the bearing 17 (the first bearing 17A or the second bearing 17B). The discharge hole 29 communicates the compression chamber 25p with the muffler chamber 19 (the first muffler chamber 19A or the second muffler chamber 19B) via the valve body 29v.

By the eccentric rotation of the roller 22, the volume of the suction chamber 25s increases. The gas refrigerant (refrigerant in the first state) is sucked into the suction chamber 25s from the accumulator 6 through the suction hole 28 . The volume of the compression chamber 25p is reduced by the eccentric rotation of the roller 22, and the gas refrigerant is compressed. If the gas refrigerant exceeds the discharge pressure, the 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 has a partition member (sealing member) 16 , a first bearing 17A, a second bearing 17B, a first muffler 18A, and a second muffler 18B.

The partition member 16 is arranged between the first compression mechanism part 20A and the second compression mechanism part 20B. The partition member 16 closes the end portion of the cylinder chamber 25 in the −Z direction of the first compression mechanism portion 20A. The partition member 16 closes the +Z direction end portion of the cylinder chamber 25 of the second compression mechanism portion 20B.

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

The second bearing (sub bearing) 17B is arranged in the −Z direction of the plurality of compression mechanism units 20 and supports the shaft 13 . The second bearing 17B closes the end portion of the cylinder chamber 25 in the -Z direction of the second compression mechanism portion 20B.

The first muffler 18A forms a first muffler chamber 19A between the first bearing 17A. The gas refrigerant compressed by the first compression mechanism unit 20A is discharged from the discharge hole 29 to the first muffler chamber 19A. The gas refrigerant discharged into the first muffler chamber 19A is discharged into the casing 11 through the muffler hole 19 e.

The second muffler 18B forms a second muffler chamber 19B between the second bearing 17B. The gas refrigerant compressed by the second compression mechanism unit 20B is discharged to the second muffler chamber 19B through a discharge hole (not shown). The second muffler chamber 19B communicates with the first 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 (refrigerant in the second state, intermediate pressure refrigerant, liquid refrigerant) introduced from the outside of the housing 11 into the cylinder chamber 25 . The injection circuit 30 has a pipe 32 , a relay valve 33 , a branch channel 34 , and an injection port 35 .

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

The relay valve 33 is provided on the piping 32 outside the casing 11 . The relay valve 33 can block the introduction of the cooling refrigerant into the casing 11 .

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

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

The effect of the injection circuit 30 will be described by comparing it with the prior art. FIG. 2 is an explanatory diagram of the function of the injection circuit 30 and is a cross-sectional view taken along line II-II of FIG. 1 . In FIG. 2 , for comparison, the injection port 35 c of the conventional art is described together with the injection port 35 of the first embodiment.

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 . Cooling refrigerant is injected into the cylinder chamber 25 from the injection port. The liquid refrigerant contained in the injected cooling refrigerant absorbs heat in the cylinder chamber 25 and evaporates. As a result, the compressed gas refrigerant and the compression mechanism unit 20 are cooled. The compressed refrigerant amount increases, and therefore, the compression performance of the rotary compressor 2 improves.

When the cooling refrigerant injected into the cylinder chamber 25 flows into the suction hole 28 , the suction amount of the gas refrigerant from the suction hole 28 into the cylinder chamber 25 decreases. As a result, the compression performance of the rotary compressor 2 decreases. At the timing of FIG. 2( b ), the front end in the eccentric direction of the roller 22 is positioned at the end 28 e of the suction hole 28 on the downstream side in the eccentric rotation direction of the roller 22 . When the injection port opens to the cylinder chamber 25 before the timing of FIG. 2( b ), the injected cooling refrigerant may flow into the suction hole 28 . It is required to close the injection port at least until the timing of (b) of FIG. 2 (hereinafter, referred to as the first 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 casing 11 . The pressure of the lubricating oil reservoir 14 accommodated inside the housing 11 is the same as the discharge pressure. As described above, the lubricating oil in the lubricating oil storage portion 14 is supplied to the sliding portion of the compressor main body 10 through the lubricating oil flow path formed along the central axis of the shaft 13 . Lubricating oil under discharge pressure exists inside the inner periphery of the roller 22 . If the injection port opens to the inside of the inner periphery of the roller 22 , lubricating oil may flow into the injection circuit 30 from the injection port. It is required that the injection port does not open to the inside of the inner circumference of the roller 22 (hereinafter referred to as the second requirement).

FIG. 4 is a graph showing the relationship between the pressure of the cooling refrigerant injected into the circuit 30 and the pressure of the compression chamber 25p. 4 is an eccentric rotation angle (sometimes 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 roller 22 in the eccentric direction in the eccentric rotation direction of the roller 22 . In FIG. 4 , the solid line indicates the pressure of the compression chamber 25p under high load, and the dotted line indicates the pressure of the compression chamber 25p under low load. The one-dot chain line indicates the pressure of the cooling refrigerant injected into the circuit 30 at high load, and the two-dot chain line indicates the pressure of the cooling refrigerant injected into the circuit 30 at low load. The high load refers to a state in which the rotary compressor 2 is operated at a high rotational speed, and the low load refers to a state in which the rotary compressor 2 is operated at a low rotational speed. When the load is high, the pressure of the refrigerant flowing through the refrigeration cycle device 1 becomes high. Along with this, the pressure of the cooling refrigerant injected into the circuit 30 increases. In addition, the pressure inside the casing 11 becomes high, and the discharge pressure of the gas refrigerant from the compression chamber 25p becomes high.

As the rotation angle θ increases, the pressure of the compression chamber 25p increases. When the load is high, the pressure of the compression chamber 25p is higher than the pressure of the cooling refrigerant injected into the circuit 30 at the time of θ=180°. If the injection port opens to the compression chamber 25p after the time of θ=180°, 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 the third requirement).

The conventional injection port 35c is opened and closed only by the end surface of the roller 22 in the Z direction. Therefore, the design freedom related to the position and opening area of the injection port 35c is small. As shown in FIG. 2( a ), the injection port 35 c is located at a position where the rotation angle θ is approximately 315°. The injection port 35c opens to the cylinder chamber 25 just at the timing of FIG. 2(b). The injection port 35c is closest to the inner circumference of the roller 22 at the time of FIG. 2(f), but does not open just inside the inner circumference. The design freedom of the injection port 35c is small, so there is a limit to designing so as to barely meet the first requirement and the second requirement.

3 is a graph showing the relationship between the eccentric rotation angle of the roller and the opening area ratio of the injection port. In the graph of FIG. 3 , the solid line is the injection port 35 of the embodiment, and the dotted line is the injection port 35c of the conventional art. The opening area ratio of the injection port on the vertical axis is normalized by setting the maximum opening area of the conventional injection port 35c to 1.

The degree of freedom in design of the injection port 35c of the prior art is small. The range of the rotation angle θ in which the injection port 35c opens with the maximum opening area becomes wider. The injection port 35c opens to the compression chamber 25p at the timing of θ=180° in (d) of FIG. 2 . As shown in FIG. 3 , the injection port 35c is not closed until the rotation angle θ becomes approximately 225°. The injection port 35c cannot satisfy the third requirement.

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

The injection port 35 of the embodiment is opened and closed by the end surfaces of the rollers 22 and the blades 40 in the Z direction. Therefore, the design freedom related to the position and opening area of the injection port 35 is large. Since the swing-type vane 40 opens and closes the injection port 35, the design freedom of the injection port 35 is extremely large. As shown in (a) of FIG. 2 , the injection port 35 is located immediately before the rotation angle θ is 360°.

(a) of FIG. 2 is the time when θ=0°. The injection port 35 is closed by the Z-direction end surface of the roller 22 . The injection port 35 is closest to the inner circumference of the roller 22, but does not open inward of the inner circumference. The injection port 35 satisfies the second requirement. Lubricating oil inside the inner circumference of the roller 22 is less likely to flow into the injection port 35 . Insufficiency of lubricating oil in the rotary compressor 2 can be suppressed.

In FIG. 2( b ), the front end in the eccentric direction of the roller 22 is located at the end 28 e of the suction hole 28 on the downstream side in the eccentric rotation direction of the roller 22 . Let the rotation angle θ in (b) of FIG. 2 be θ1. The injection port 35 is closed by the Z-direction end surface of the roller 22 . The injection port 35 satisfies the first requirement.

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

(d) of FIG. 2 is the time when θ=180°. The entire injection port 35 is closed by the Z-direction end surface of the vane 40 . In FIG. 2( e ) and FIG. 2 ( f ) where 180°<θ, the injection port 35 is closed by the end surface of the vane 40 or the roller 22 in the Z direction. The injection port 35 satisfies the third requirement. When the load is high, it is difficult for the gas refrigerant compressed by the cylinder chamber 25 to flow into the injection circuit 30 from the injection port 35 .

As shown in FIG. 4 , at low load, the pressure of the compression chamber 25 p is higher than the pressure of the cooling refrigerant injected into the circuit 30 when the rotation angle θ is 140°. 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 conventional injection port 35c. When 140°<θ, the opening area ratio of the injection port 35 of the embodiment is smaller than that of the conventional injection port 35c. Even when the load is low, the gas refrigerant compressed by the cylinder chamber 25 hardly flows 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 according to the embodiment is twice that of the conventional injection port 35 c. The pressure loss of the cooling refrigerant at the injection port 35 can be suppressed. A sufficient amount of cooling refrigerant can be injected into the cylinder chamber 25 . The cooling performance and compression performance of the rotary compressor 2 are improved.

As shown in FIG. 2( b ), the angle from the center of the throat 43 (or vane housing hole 41 ) to the end 28e of the suction hole 28 in the eccentric rotation direction of the roller 22 is θ1. As shown in (c) of FIG. 2 , the angle from the center of the throat 43 (or vane housing hole 41 ) to the tip of the roller 22 in the eccentric direction with the largest opening area of the injection port 35 is θmax. At this time, the following Mathematical Expression 1 is established.

θ1<θmax<140°...(1)

As shown in FIG. 3, θ1 is about 30°. θmax is approximately 90°<θmax<110°. θmax satisfies Mathematical Expression 1.

When θ1<θmax, the opening area of the injection port 35 becomes maximum after the tip of the roller 22 in the eccentric direction passes through the end 28e of the suction hole 28 . Before this, the opening area of the injection port 35 does not become the maximum, so the inflow of the cooling refrigerant into the suction hole 28 can be suppressed.

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

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

The design freedom of the injection port 35 is large. After the pressure of the gas refrigerant in the cylinder chamber 25 becomes higher than the pressure of the cooling refrigerant, the injection port 35 does not open to the cylinder chamber 25 . It is difficult for the gas refrigerant to flow into the injection port 35 . The compression performance of the rotary compressor 2 is improved.

The blade 40 is integral with the roller 22 .

Since the swing-type vane 40 opens and closes the injection port 35, the design freedom of the injection port 35 is extremely large. 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 injection port 35 can be closed without a gap.

The transition of the injection port 35 from the closed state to the state with the largest opening area 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 injection port 35 is opened only by the end surface of the roller 22 on the partition member 16 side in a short time. The pressure loss of the cooling refrigerant can be suppressed, and a sufficient amount of cooling refrigerant can be injected into the cylinder chamber 25 . The cooling performance and compression performance of the rotary compressor 2 are improved.

The angle from the center of the throat 43 (or 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 θ1. In the eccentric rotation direction of the roller 22 , the angle of the front end of the roller 22 in the eccentric direction from the center of the throat 43 (or vane housing hole 41 ) to the opening area of the injection port 35 with the largest opening area is θmax. At this time, θ1<θmax<140° holds true.

When θ1<θmax, the inflow of the cooling refrigerant into the suction hole 28 can be suppressed. When θmax<140°, the inflow of the compressed gas refrigerant into the injection port 35 can be suppressed. The compression performance of the rotary compressor 2 is improved.

The refrigeration cycle apparatus 1 of the first embodiment includes the above-mentioned rotary compressor 2 , radiator 3 , expansion device 4 , and heat absorber 5 . The radiator 3 is connected to the rotary compressor 2 . The expansion device 4 is connected with the radiator 3 . The heat absorber 5 is connected between the expansion device 4 and the rotary compressor 2 .

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

(second embodiment)

A rotary compressor according to a second embodiment will be described.

FIG. 5 is a cross-sectional view of a portion corresponding to line II-II in FIG. 1 . The rotary compressor of the second embodiment is different from the first embodiment of the swing type in that it is a rotary type. The description of the second embodiment of the part having the same configuration as that of the first embodiment is omitted.

The rotary compressor of the second embodiment is a so-called rotary rotary compressor in which the vanes 50 and the rollers 22 are separated.

As shown in (c) of FIG. 5 , the blade 50 has a flat plate shape. The cylinder 24 has a vane groove 51 as a vane receiving hole, and supports the vane 50 so as to be able to advance and retreat in the cylinder chamber 25 . The vane 50 is arranged inside the vane groove 51 . The blade 50 is movable in the X direction along the blade groove 51 . A lubricating oil hole 52 is formed at an end portion of the vane groove 51 in the −X direction. The lubricating oil in the lubricating oil reservoir 14 is introduced into the lubricating oil hole 52 . As mentioned above, lubricating oil is discharge pressure. The vane 50 is urged 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 from the vane groove 51 relative to the cylinder chamber 25 with the eccentric rotation of the roller 22 .

The injection circuit has an injection port 37 .

The injection port 37 has an oblong shape or an 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 area of the partition member 16 with respect to the vane 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 arranged 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 rotates most eccentrically in the -X direction, the injection port 37 is arranged 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 rotates most eccentrically in the +X direction, the injection port 37 is arranged between the outer periphery of the roller 22 and the outer periphery of the cylinder chamber 25 in the X direction. The injection port 37 opens to the cylinder chamber 25 between the tip of the vane 50 and the outer peripheral surface of the roller 22 as described below.

The function of the injection circuit will be described.

Fig. 5 is an explanatory diagram of the operation of the injection circuit, and is a cross-sectional view of a portion corresponding to line II-II in Fig. 1 . The injection port 37 is opened and closed by the end surfaces of the rollers 22 and the blades 50 in the Z direction. Therefore, the design freedom of the injection port 37 is large.

(a) of FIG. 5 is the time when θ=0°. The injection port 37 is closed by the Z-direction end surface of the roller 22 . The injection port 37 is closest to the inner circumference of the roller 22, but does not open inward of the inner circumference. The injection port 37 satisfies the second requirement. Lubricating oil inside the inner circumference of the roller 22 is less likely to flow into the injection port 37 . Insufficiency of lubricating oil in the rotary compressor can be suppressed.

At the timing between (a) and (b) of FIG. 5 , the tip of the roller 22 in the eccentric direction passes through the end 28e of the suction hole 28 . The injection port 37 is closed by the Z-direction end surface of the roller 22 until this point of time. The injection port 37 satisfies the first requirement.

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

(c) of FIG. 5 is the time when θ=180°, which is the second half of the compression process of the cylinder chamber 25 . The entire injection port 37 is closed by the Z-direction end surface of the vane 50 .

(d) of FIG. 5 is the time when θ=270°. The roller 22 rotates eccentrically toward the compression chamber 25 p side of the reference line 44 . The gap between the front end of the vane 50 and the outer peripheral surface of the roller 22 is smaller on the side of the compression chamber 25p than on the side of the suction chamber 25s of the reference line 44 . The injection port 37 is arranged on the compression chamber 25p side of the reference line 44 in the Y direction. Between the front end of the vane 50 and the outer peripheral surface of the roller 22, the opening area of the injection port 37 to the cylinder chamber 25 becomes small. The inflow of the gas refrigerant compressed in the cylinder chamber 25 from the injection port 17 to the injection circuit decreases. In the range of 180°<θ, the injection port 37 is almost closed. The injection port 37 satisfies the third requirement. When the load is high, it is difficult for the gas refrigerant compressed by the cylinder chamber 25 to flow into the injection circuit from the injection port 37 .

As in the first embodiment, 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 θ1. The angle from the center of the vane groove 51 to the tip of the roller 22 in the eccentric direction at which the opening area of the injection port 37 becomes the largest is θmax. At this time, θ1<θmax<140° holds true.

As described in detail above, in the rotary compressor of the second embodiment shown in FIG. 5( c ), the vane 50 and the roller 22 are separate bodies. The injection port 37 is formed at a position closer to the compression chamber 25p than the center in the Y direction in the region where the partition member 16 slides with respect to the vane 50 . The injection port 37 opens to the cylinder chamber 25 between the front end of the vane 50 on the cylinder chamber 25 side and the outer peripheral surface of the roller 22 .

The design freedom of the injection port 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 cooling refrigerant is injected into the cylinder chamber 25 . In the second half of the compression process, the opening area of the injection port 37 becomes smaller, and it becomes difficult for the compressed gas refrigerant to flow from the injection port 37 into the injection circuit 30 . 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 at which the injection port 37 opens to the cylinder chamber 25 can be adjusted. A sufficient amount of cooling refrigerant is injected into the cylinder chamber 25 .

(third embodiment)

A rotary compressor according to a third embodiment will be described.

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

As shown in FIG. 7 , the rotary compressor of the third embodiment is of the same rotary type as that of the second embodiment. As shown in FIG. 6 , the third embodiment is different from the second embodiment in which the injection port 37 is the opening of the branch flow path in that the injection port 37 is the opening of the first recess 61 . The description of the third embodiment of the part having the same configuration as that of the second embodiment is omitted.

The injection circuit has an injection port 37 , a first recess 61 , a second recess 62 , a third recess 63 , a distribution channel 64 , and a pipe 32 . Hereinafter, the injection port 37, the first concave portion 61, the second concave portion 62, and the third concave portion 63 formed on the side of the first compression mechanism portion 20A will be described, but these members are formed in the same manner on the side of the second compression mechanism portion 20B. .

The injection port 37 is an opening of the first recess 61 .

The first concave portion 61 is formed on the end surface of the partition member 16 on the side of the first compression mechanism portion 20A.

The second concave portion 62 is formed on the end surface of the blade 50 on the side of the partition member 16 . The opening of the second recess 62 is closed by the partition member 16 . The second concave portion 62 extends in the X direction from the central portion of the blade 50 in the X direction toward the end portion in the +X direction. The end portion in the +X direction of the second concave portion 62 can communicate with the first concave portion 61 .

The third concave portion 63 is formed on the end surface of the partition member 16 on the side of the first compression mechanism portion 20A. The opening of the third concave portion 63 is closed by the cylinder 24 of the first compression mechanism portion 20A. As shown in FIG.7(b), the 3rd recessed part 63 extends along a Y direction. The end of the third recess 63 opens to the vane groove 51 formed in the cylinder 24 .

The piping 32 extends from the outside to the inside of the casing 11 . The pipe 32 is disposed in the cylinder 24 of the first compression mechanism unit 20A.

As shown in FIG. 6 , the distribution channel 64 extends in the −Z direction from the tip of the pipe 32 . The distribution flow path 64 communicates with the third recessed portion 63 formed in the partition member 16 on the side of the first compression mechanism portion 20A. The distribution channel 64 penetrates the partition member 16 along the Z direction. The distribution flow path 64 communicates with the third recessed portion 63 formed on the second compression mechanism portion 20B side of the partition member 16 .

The function of the injection circuit will be described.

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

(a) of FIG. 7 is the time when θ=0°. The blade 50 is moved maximally in the -X direction. The end portion in the +X direction of the second concave portion 62 does not communicate with the first concave portion 61 . The injection port 37 is closed by the Z-direction end surface of the roller 22 . The cooling refrigerant is not injected into the cylinder chamber 25 from the injection port 37 .

(b) of FIG. 7 is the time when θ=90°. The blade 50 moves in the +X direction. The end portion in the −X direction of the second recess 62 communicates with the third recess 63 , and the end portion in the +X direction communicates with the first recess 61 . The pipe 32 , the distribution channel 64 , the third recess 63 , the second recess 62 , the first recess 61 , and the injection port 37 communicate in this order. Between the tip of the vane 50 and the outer peripheral surface of the roller 22 , the injection port 37 opens to the cylinder chamber 25 . Cooling refrigerant is injected into the cylinder chamber 25 from the injection port 37 .

(c) of FIG. 7 is the time when θ=180°. The blade 50 moves maximally in the +X direction. The end portion of the second concave portion 62 in the −X direction does not communicate with the third concave portion 63 . The injection port 37 is closed by the Z-direction end surface of the vane 50 . The cooling refrigerant is not injected into the cylinder chamber 25 from the injection port 37 .

(d) of FIG. 7 is the time when θ=270°. The blade 50 moves in the -X direction. The end portion in the −X direction of the second recess 62 communicates with the third recess 63 , and the end portion in the +X direction communicates with the first recess 61 . As in the second embodiment, the opening area of the injection port 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 from the injection port 17 to the injection circuit decreases.

Also in the third embodiment, as in the second embodiment, the cooling refrigerant is intermittently injected from the injection port 37 into the cylinder chamber 25 .

As described in detail above, in the rotary compressor of the third embodiment shown in FIG. 6 , the injection port 37 is an opening formed in the first recess 61 of the partition member 16 . The blade 50 has a second recess 62 that can communicate with the first recess 61 on the end surface on the side of the partition member 16 .

The piping 32 for the cooling refrigerant injected into the circuit can be arranged in the cylinder 24 instead of the partition member 16 . In addition to the bearing 17 , a discharge hole 29 for the cylinder chamber 25 may be formed in the partition member 16 . The compression performance of the rotary compressor is improved.

In the above-mentioned embodiment, the rotary compressor 2 has the two compression mechanism parts 20 (the first compression mechanism part 20A and the second compression mechanism part 20B). On the other hand, the rotary compressor 2 may have only one compression mechanism unit 20 or may have three or more compression mechanism units 20 .

In addition, in the above-mentioned embodiment, the rotary compressor that cools the compression mechanism unit by injecting liquid refrigerant has been described, but a rotary compressor that injects a gas refrigerant at an intermediate pressure may also be used. Accordingly, it is possible to obtain a rotary compressor that suppresses a decrease in reliability, improves energy saving, and increases cooling and heating capabilities.

According to at least one embodiment described above, there are injection ports 35 and 37 opened and closed by the rollers 22 and the end faces of the vanes 40 and 50 on the side of the partition member 16 . Thereby, the compression performance of the rotary compressor can be improved.

It is not limited to the refrigeration cycle apparatus 1 using the rotary compressor 2 of this embodiment. In the rotary compressor 2 of the above-mentioned embodiment, the configuration using two cylinders has been described, but it is not limited thereto. There may be one cylinder, or three or more cylinders.

In addition, the first bearing 17A or the second bearing 17B may be used as a sealing member, and the injection ports 35 and 37 may be provided in the first bearing 17A or the second bearing 17B.

Although some embodiments of the present invention have been described, these embodiments are shown as examples and are not intended to limit the scope of the invention. These embodiments can be implemented in other various forms, and various omissions, substitutions, and changes can be made without departing from the scope of the invention. These embodiments and modifications thereof are included in the scope and spirit of the invention, and are included in the invention described in the claims and the scope equivalent thereto.

Claims (8)

1. A rotary compressor wherein, Has a housing that accommodates the shaft and the compression mechanism inside, The above-mentioned compression mechanism unit has: The eccentric part is arranged on the above-mentioned shaft; A cylinder having a cylinder chamber for the above-mentioned eccentric portion; The roller is cylindrical, embedded in the above-mentioned eccentric part, and rotates eccentrically in the above-mentioned cylinder chamber; The vane moves forward and backward with the eccentric rotation of the roller, and divides the cylinder chamber into a suction chamber and a compression chamber for the refrigerant in the first state; a closing member closing an end portion of the cylinder chamber in the axial direction of the shaft; and An injection port is formed in the closing member, opens to the cylinder chamber, and injects the refrigerant in the second state introduced from the outside of the casing into the cylinder chamber, The injection port is opened and closed by the roller and the end surface of the vane on the closing member side. 2. The rotary compressor according to claim 1, wherein: The blades are integrated with the rollers. 3. The rotary compressor according to claim 1 or 2, wherein: The filling port transitions from the closed state to the state with the largest opening area only through the end surface of the roller on the closing member side. 4. The rotary compressor according to claim 1, wherein: The vane is separate from the roller, and is movable in a first direction along a vane groove formed in the cylinder, and the front end of the cylinder chamber side in the first direction is in contact with the outer peripheral surface of the roller, The injection port is formed at a position closer to the compression chamber than a center in a second direction perpendicular to the axial direction and the first direction in a region of the closing member that slides relative to the vane, The injection port is open to the cylinder chamber between the front end of the vane on the cylinder chamber side and the outer peripheral surface of the roller. 5. The rotary compressor according to claim 4, wherein: The length of the injection port in the first direction is longer than the length in the second direction. 6. The rotary compressor according to claim 4 or 5, wherein: The injection port is an opening formed in the first recess of the closure member, The vane has a second recess capable of communicating with the first recess on an end surface on the closing member side. 7. The rotary compressor according to any one of claims 1 to 6, wherein: 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 first state into the cylinder chamber, Where, in the eccentric rotation direction of the roller, the angle from the center of the vane housing hole to the end of the suction hole on the downstream side in the eccentric rotation direction of the roller is θ1, In the eccentric rotation direction of the roller, when the angle from the center of the vane housing hole to the opening area of the injection port at which the tip of the roller becomes the largest in the eccentric direction is θmax, θ1<θmax<140° is established. 8. A refrigeration cycle device, comprising: A rotary compressor as claimed in any one of claims 1 to 7; a radiator connected to the aforementioned rotary compressor; an expansion device, connected to said radiator; and A heat absorber is connected between the expansion device and the rotary compressor.

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