JP2012145121A - Refrigerant gas suction amount controller in rotary compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To properly control a refrigerant gas flow rate to be sucked into a compression chamber of a rotary compressor, in both a low-speed rotation area and a high-speed rotation area.SOLUTION: In the low-speed rotation area, a reed valve 55 keep a planar state with its elasticity, and separates from a valve seat 54. A refrigerant gas flows through all the opening areas of the through-hole 58 of the reed valve 55 and the through-hole 58 of the valve seat 54, and is sucked into a suction chamber 16. Hence, a necessary flow rate of the refrigerant gas is fully secured. In the high-speed rotation area, the reed valve 55 is brought into contact with the valve seat 54 by the pressure of the refrigerant gas. The through-hole 58 of the valve seat 54 and the through-hole 58 of the reed valve 55 are communicated with a suction port 17, with their opening areas throttled. As a result, the refrigerant gas of a high flow rate is adjusted to a predetermined low flow rate by a throttle valve 50 and is sucked into the suction chamber 16, The generation of an excessive cooling capacity is prevented thereby.

Description

  The present invention relates to a suction amount control device capable of adjusting a suction amount of refrigerant gas in a low speed rotation region and a high speed rotation region of a rotary compressor.

  Patent Document 1 has been devised in order to suppress excessive cooling capacity during high-speed rotation of a vane compressor, and the following configuration is disclosed. In the vane compressor, a reed valve having a valve portion having an area smaller than the opening area of the suction port or the inlet is disposed at the inlet of the flow passage communicating with the suction port or the suction port of the compression chamber.

  When the reed valve rotates at a low speed with a small amount of gas sucked into the compression chamber, the reed valve is maintained in a state in which the opening of the suction passage is large and exhibits a sufficient cooling capacity. On the other hand, when the rotation rises, the reed valve is rotated in the direction of continuously reducing the opening of the suction passage by increasing the amount of suction gas, and acts to suppress the amount of gas sucked into the compression chamber. Therefore, the technique disclosed in Patent Document 1 can prevent an excessive cooling capacity during high-speed rotation.

  Patent Document 2 discloses a configuration of a spool type throttle valve as an oil amount adjusting valve. That is, a valve body chamber having a larger diameter than the pressure oil passage and coaxial with the pressure oil passage is formed in the middle of the pressure oil passage of the valve body. In the valve body chamber, a bottomed cylindrical valve body having a diameter larger than that of the pressure oil passage is pushed by the flow of pressure oil and is slidable by a predetermined distance. The bottom wall of the valve body is provided with a through hole that is eccentric with respect to the axis of the pressure oil passage.

  When the pressure oil flows in the pressure oil passage from the bottom wall side of the valve body to the opening side, the valve body is moved by the pressure oil, and the bottom wall of the valve body is separated from the wall surface of the valve body chamber. For this reason, the pressure oil can flow by the opening area of the through hole of the valve body. On the other hand, when the pressure oil flows in the pressure oil passage from the opening side of the valve body to the bottom wall side, that is, in the opposite direction, the valve body moves to the opposite side, and the bottom wall of the valve body moves to the valve body chamber. Abuts against the wall surface. Since the through hole is eccentric with respect to the pressure oil passage, a part of the through hole is closed, the opening area of the through hole is reduced, and the flow rate of the pressure oil flow is reduced. Therefore, the technique disclosed in Patent Document 2 can adjust the flow rate of the pressure oil flowing in the forward and reverse directions to a different flow rate by one oil amount adjusting valve.

Japanese Utility Model Publication No. 2-137588 Japanese Utility Model Publication No. 57-48367

  In the technique disclosed in Patent Document 1, the reed valve is rotated by the pressure of the suction gas whose flow rate has increased during high-speed rotation, and the valve portion closes a part of the suction port or the inlet to narrow the passage of the suction gas. It is a configuration. In addition, the reed valve opens during low-speed rotation and acts to increase the flow rate of the intake gas. However, when the reed valve is opened, the suction gas has to go around the valve portion and pass through the suction port or inlet, so that the valve portion becomes a resistance and a sufficient flow rate cannot be secured. is there.

  For the reasons described above, if the intake gas flow rate is sufficiently reduced during high-speed rotation, the intake gas passage during low-speed rotation is narrowed, and conversely if the intake gas passage during low-speed rotation is widened, A contradictory phenomenon that the intake gas passage cannot be sufficiently throttled during high-speed rotation is likely to occur, and adjustment of the intake gas flow rate is difficult. Therefore, with the technique disclosed in Patent Document 1, it is difficult to secure an appropriate amount of intake gas in all regions from low speed rotation to high speed rotation.

  The technique disclosed in Patent Document 2 is a configuration in which the flow of pressure oil is reduced by a cylindrical valve body having a through hole that is eccentric with respect to the pressure oil passage. However, the throttle effect by the valve element is generated only in the case of one flow of the pressure oil flowing in the forward and reverse directions in the pressure oil passage, and the same throttle effect is always generated for one flow. . Further, in order to eliminate the throttling effect, the flow of pressure oil must be reversed and changed in the other direction. Therefore, the technique disclosed in Patent Document 2 is difficult to apply to a rotary compressor that requires adjustment of the flow rate of refrigerant gas flowing in one direction from the low-speed rotation region to the high-speed rotation region.

  An object of the present invention is to enable appropriate control of the flow rate of refrigerant gas sucked into a compression chamber of a rotary compressor in a low-speed rotation region and a high-speed rotation region.

  The invention of claim 1 is directed to a refrigerant gas suction portion including a suction port, a suction passage, and a suction chamber, a compression portion including a compression mechanism for the refrigerant gas, and a refrigerant gas including a discharge port, a discharge passage, and a discharge chamber. In the rotary compressor having a discharge part, a throttle valve comprising a valve seat and a valve body that can approach and separate from the valve seat is disposed in the suction part, and the refrigerant is provided in the valve seat and the valve body, respectively. A through hole penetrating in the gas flow direction is formed, and at least the central axis of one of the valve seat and the valve body is arranged eccentrically from the central axis of the suction portion, and the valve body is an elastic body The valve seat is formed by a rigid valve seat against which the reed valve abuts, and the valve body is urged away from the valve seat and the flow rate of the refrigerant gas increases to increase the flow rate. That they were approaching the valve seat And butterflies.

According to the first aspect of the present invention, in the low-speed rotation region, the valve body is separated from the valve seat, and the flow resistance of the refrigerant gas is small due to the presence of the through hole of the valve body, so that the refrigerant gas has a sufficient suction amount. Adjusted to On the other hand, in the high-speed rotation region, the opening area of the through hole is reduced by the valve body coming into contact with the valve seat, and the refrigerant gas is adjusted to an appropriate suction amount. As a result, the optimum cooling capacity can be obtained in the entire rotation region from the low-speed rotation region to the high-speed rotation region.
In addition, since the valve body is constituted by a reed valve made of an elastic body, and the valve seat is formed by a rigid valve seat against which the reed valve abuts, a through hole is formed in a known reed valve. Therefore, the throttle valve can be easily obtained.

  The invention according to claim 2 is characterized in that the throttle valve including the valve seat and the valve body is unitized, so that the operation of attaching the throttle valve to the rotary compressor is facilitated. Further, it can be easily mounted on an existing compressor.

  The present invention according to claim 3 is characterized in that the valve seat is formed separately from the suction portion and is attached to the suction portion. It becomes free, and it becomes easy to set the amount of throttling of the through hole.

  The invention of claim 4 is characterized in that the valve seat and the through hole of the valve body are formed by a perfect circle, so that the amount of throttling of the through hole of the valve body can be maximized.

  The invention of claim 5 is characterized in that the valve seat and the through hole of the valve body are formed by an ellipse. Therefore, the opening area of the through hole through which the refrigerant gas passes can be increased in the low speed rotation region. it can.

  The present invention provides a rotary compressor that has a sufficient amount of refrigerant gas sucked in a low speed rotation region to exhibit an appropriate cooling capacity, and has an excessive cooling capacity by reducing the amount of refrigerant gas sucked in a high speed rotation region. Can be prevented.

It is a longitudinal cross-sectional view of the vane type compressor which shows embodiment of this invention. FIG. 2 is an enlarged view of the throttle valve in FIG. 1, (a) is a longitudinal sectional view, and (b) is a plan view of (a).

  The present embodiment shown in FIGS. 1 and 2 is configured as follows. As shown in FIG. 1, a vane compressor housing 1 is integrally formed with a front housing 2 located on the left side of the figure and a bottomed tubular rear housing 3 located on the right side of the figure. Has been. A cylinder block 5 having an oval cylindrical inner peripheral surface 4 is accommodated inside the front side of the rear housing 3, and a front side plate 6 and a rear side plate 7 are fitted and fixed to both front and rear end surfaces. A rotating shaft 8 is supported on the front side plate 6 and the rear side plate 7 via a radial bearing 9.

  A rotor 10 is fitted and fixed to the rotary shaft 8 so as to be located in the cylinder block 5. The rotor 10 is formed with vane grooves 11 radially at a plurality of locations, and vanes 12 are accommodated in the vane grooves 11 so as to be able to appear and retract. A crescent-shaped space formed between the inner peripheral surface 4 of the cylinder block 5 and the outer peripheral surface of the rotor 10 is partitioned into a plurality of working chambers 13 by the vanes 12. Although not shown in the drawing, two crescent-shaped spaces forming the working chamber 13 are formed at two positions with respect to the rotating shaft 8. The rotor 10, the vane groove 11 and the vane 12 constitute a refrigerant gas compression mechanism in the present invention. In addition, the compression mechanism of the present invention is configured by including the working chamber 13 in the compression mechanism.

  When the rotor 10 rotates, the tip surface of the vane 12 contacts the inner peripheral surface 4 of the cylinder block 5 by centrifugal force. A stroke in which the working chamber 13 expands in volume with respect to the rotation direction of the rotor 10 is a suction stroke, and a stroke in which the working chamber 13 decreases is a compression stroke. The working chamber 13 during the suction stroke communicates with a suction chamber 16 in the front housing 2 through a suction passage 14 provided in the cylinder block 5 and a suction passage 15 provided in the front side plate 6 communicating with the suction passage 14. The suction chamber 16 communicates with a suction port 17 connected to an external refrigerant circuit (not shown) and sucks refrigerant gas.

  A discharge chamber 18 is defined in the outer periphery of the cylinder block 5 together with the rear housing 3 and the side plates 6 and 7. A plurality of discharge ports 19 are formed in the cylinder block 5 to communicate the working chamber 13 and the discharge chamber 18 during the compression stroke. These discharge ports 19 can be opened and closed by a discharge valve 20. Note that the release position of the discharge valve 20 is restricted by the retainer 21.

  The rear side plate 7 is formed with a small-diameter throttle passage 22 penetrating in the direction of the rotary shaft 8 and communicates with the discharge chamber 18. Further, a grooved discharge passage 23 is formed on the rear side surface of the rear side plate 7. The discharge passage 23 has one end communicating with the throttle passage 22 and the other end communicating with an oil storage chamber 24 formed between the rear side plate 7 and the rear housing 3. The oil storage chamber 24 communicates with an external refrigerant open circuit (not shown) through a discharge port 25 formed in the rear housing 3.

  An oil separator 26 is provided in the upper part of the oil storage chamber 24 in order to separate the mist-like lubricating oil in the refrigerant gas supplied from the discharge passage 23. A case 27 constituting the oil separator 26 is fixed to the rear side plate 7 so as to cover the rear end of the rotating shaft 8 and the discharge passage 23. The case 27 includes a bottomed cylindrical oil separation chamber 28 and a cylindrical oil separation cylinder 29 fitted and fixed to the top thereof, and has an oil passage 30 communicating with the oil storage chamber 24 on the bottom surface of the oil separation chamber 28. . Further, a passage 31 that penetrates in the direction of the rotation shaft 8 is formed in the case 27. One end of the passage 31 communicates with the lower outlet 32 of the discharge passage 23, and the other end is directed to the outer peripheral surface of the oil separation cylinder 29. The discharge chamber 18, the discharge port 19, the throttle passage 22, the discharge passage 23, the discharge port 25, and the passage 31 constitute a discharge portion of the present invention.

  An oil guide plate 33 formed in a roof shape (not shown) as viewed from the rear side is provided in the lower portion of the oil passage 30 of the case 27 so as to protrude in the axial direction. The guide plate 33 has a function of guiding oil dropped from the oil passage 30 of the oil separation chamber 28 downward and stabilizing the oil level stored in the oil storage chamber 24. An oil supply passage 34 is formed in the rear side plate 7, and the oil stored in the oil storage chamber 24 is introduced into the radial bearing 9, the vane groove 11 and the like for lubrication.

  The throttle valve 50 is provided in the suction port 17 of the vane compressor. The suction port 17 is formed in a large-diameter suction passage 51 whose upstream inlet side has the same central axis as the central axis X3 of the suction port 17. In the suction passage 51, a connection portion with the suction port 17 is formed in a stepped shape, a right portion (see FIGS. 1 and 2A) of the drawing is formed in the high pedestal portion 52, and a left portion is formed in the low pedestal portion 53. Is formed.

  A base end side of a plate-shaped valve seat 54 and a reed valve 55 corresponding to the valve body of the present invention is fixed to the high pedestal portion 52 by bolts 56. The valve seat 54 and the reed valve 55 are formed in a substantially rectangular shape (see FIG. 2A) and have dimensions that can completely cover the suction port 17. The valve seat 54 is made of a rigid body, is plastically deformed in a curved shape, and is in contact with the lower pedestal portion 53 at the distal end side. A through hole 57 is formed in the valve seat 54, and the through hole 57 has a central axis X 1 that is eccentric with respect to the central axis X 3 of the suction port 17 and the suction passage 51. The reed valve 55 is made of an elastic body, and as shown by the solid line in FIG. Therefore, the reed valve 55 is separated from the valve seat 54 by a certain distance in a normal state. A through hole 58 is formed in the reed valve 55, and the through hole 58 has a central axis X2 that is eccentric from the central axis X3 so as to be at a position different from the central axis X1.

  The constant distance in this case is a distance at which the throttle action by the valve seat 54 and the reed valve 55 does not occur. The eccentric distances of the central axis X1 of the through hole 57 and the central axis X2 of the through hole 58 with respect to the central axis X3 of the suction passage 51 can be variously set according to the amount of restriction required when the vane compressor is operated. Moreover, although the opening areas of the through holes 57 and 58 are set to be the same, they may be set to be different areas as necessary. The use of different opening areas can increase the degree of freedom for setting the aperture amount.

The present embodiment configured as described above operates as follows.
The general operation of the vane compressor will be described. Since the rotary shaft 8 is rotated by the power of the engine, the rotor 10 and the vane 12 are rotated, and the refrigerant gas flowing into the suction chamber 16 from the suction port 17 flows into the suction passage. The air is sucked into the working chamber 13 during the suction stroke through 15 and 14. The refrigerant gas in the working chamber 13 is compressed by the volume reduction of the working chamber 13 that has entered the compression stroke. The compressed refrigerant gas is discharged into the discharge chamber 18 through the discharge port 19 and the discharge valve 20.

  Discharge pulsation generated by intermittently discharging the refrigerant gas into the discharge chamber 18 is suppressed by the discharged refrigerant gas flowing into the discharge passage 23 via the throttle passage 22. The refrigerant gas flowing through the discharge passage 23 is blown from the passage 31 of the oil separator 26 to the outer peripheral surface of the oil separation cylinder 29 and guided to the oil separation chamber 28 while turning around the outer periphery of the oil separation cylinder 29. For this reason, the oil is separated from the refrigerant gas, and the separated oil is dropped from the oil passage 30 into the oil storage chamber 24. The refrigerant gas from which the oil has been separated flows upward through the oil separation cylinder 29 and is introduced from the upper space of the oil storage chamber 24 into the discharge port 25.

  The vane compressor fluctuates between a low speed rotation region and a high speed rotation region in proportion to the engine speed. The reed valve 55 maintains a planar state by its own elastic force in the low rotation region of the vane compressor, and is separated from the valve seat 54. Accordingly, since the refrigerant gas can flow through the entire opening area of the through holes 58 and 59, a sufficient flow rate can be sucked into the suction chamber 16. For this reason, the vane type compressor can sufficiently secure the necessary flow rate of the refrigerant gas in the low speed rotation region.

  On the other hand, when the vane compressor is operated in the high-speed rotation region, the reed valve 55 resists its own elastic force as shown by the solid line in FIG. Then, it bends to the downstream side of the suction passage 51 and approaches the valve seat 54. Since the eccentric through hole 58 overlaps the eccentric through hole 57, the opening area S3 (see FIG. 2B) through which the refrigerant gas can pass is greatly reduced, and the flow rate of the refrigerant gas is suppressed. Therefore, the high flow rate refrigerant gas flowing into the inlet of the throttle valve 50 is adjusted to a low flow rate set in advance by the throttle valve 50 and sucked into the suction chamber 16, thereby preventing the occurrence of excessive cooling capacity. As described above, in this embodiment, by configuring the throttle valve using the reed valve having the through hole 58, it is possible to obtain an appropriate cooling capacity in the entire rotation region of the vane compressor with a simple configuration. Further, since the refrigerant gas flows through the through holes 57 and 58, the flow resistance is reduced.

  Thus, the vane type compressor in the present embodiment can secure an appropriate amount of refrigerant gas in the entire region from the low-speed rotation region to the high-speed rotation region, and obtain an optimal cooling capacity.

The above-described embodiment has the following operational effects.
(1) Since the amount of refrigerant gas sucked in the low-speed rotation region and the high-speed rotation region can be appropriately controlled, optimum cooling capacity can be obtained in the entire rotation region.
(2) Since the valve seat 54 and the reed valve 55 of the throttle valve 50 are provided with through holes 57 and 58 having a center axis eccentric with respect to the center axis X3 of the suction passage 51, the flow resistance of the refrigerant gas is reduced. There are few and efficient diaphragm functions can be obtained.
(3) Since the through holes 57 and 58 of the valve seat 54 and the reed valve 55 are both eccentric with respect to the suction passage 51, the degree of freedom in setting the throttle amount can be increased.
(4) Since the through holes 57 and 58 of the valve seat 54 and the reed valve 55 are formed in a perfect circle, the configuration of the throttle valve 50 is simplified and reduced in size, and the mountability to the vane compressor is improved. be able to.

  The present invention is not limited to the configuration of the above-described embodiment, and various modifications are possible within the scope of the spirit of the present invention, and can be implemented as follows.

(1) In the present embodiment, the center axis X1 and X2 of the through holes 57 and 58 of the valve seat 54 and the reed valve 55 are both described as being eccentric from the center axis X3 of the suction port 17. The effect of the present invention can be obtained even when only the central axis of the through hole of either the valve seat or the valve body is eccentric.
(2) In the present embodiment, a separate valve seat 54 independent of the suction port 17 constituting the suction portion is mounted on the suction port 17, but a part of the inner wall of the suction port 17 is processed. It is possible to constitute a valve seat. In this case, since the through hole formed in the valve seat also serves as the suction port 17, the central axis of the through hole of the valve seat coincides with the central axis of the suction port 17, and the central axis of the through hole of the valve body Only eccentric.
(3) The throttle valve 50 including the valve seat 54 and the reed valve 55 may be unitized, thereby facilitating the work of attaching the throttle valve 50 to the vane compressor. Further, it can be easily mounted on an existing compressor.

(4) The throttle valve 50 described in the present embodiment or the modified example can be disposed in the suction passages 14 and 15 or the suction chamber 16 shown in FIG.
(5) The through holes 57 and 58 of the valve seat 54 and the reed valve 55 or the suction port 17 and the suction passages 14, 15 and 51 are not limited to a perfect circle but can be formed as an ellipse or a square hole. When the through holes 57 and 58 are formed in an elliptical shape, the opening area of the through hole 57 serving as a refrigerant gas passage (the same applies to the through hole 58) can be made larger than that of a perfect circle. It is easy to secure the flow rate of the refrigerant gas even in the reduced throttle valve.
(6) The present invention can be implemented not only in a vane compressor but also in a rotary compressor such as a scroll compressor, a screw compressor, or a roots compressor.

DESCRIPTION OF SYMBOLS 1 Housing 2 Front housing 3 Rear housing 8 Rotating shaft 10 Rotor 11 Vane groove 12 Vane 13 Working chamber 14, 15, 51 Suction passage 16 Suction chamber 17 Suction port 18 Discharge chamber 25 Discharge port 50 Throttle valve 54 Valve seats 57, 58 Through Hole 55 Reed valves S1, S2, S3 Open area X1, X2, X3 Central axis

Claims (5)

In a rotary compressor including a refrigerant gas suction portion including a suction port, a suction passage, and a suction chamber, a compression portion including a compression mechanism of the refrigerant gas, and a refrigerant gas discharge portion including a discharge port, a discharge passage, and a discharge chamber ,
A throttle valve comprising a valve seat and a valve body that can approach and separate from the valve seat is disposed in the suction portion, and through holes that respectively penetrate in the refrigerant gas flow direction are formed in the valve seat and the valve body. And at least a central axis of one of the through hole of the valve seat and the valve body is arranged eccentrically from a central axis of the suction portion, and the valve body is constituted by a reed valve made of an elastic body, Is formed by a rigid valve seat against which the reed valve abuts, and the valve body is urged in a direction away from the valve seat and is brought closer to the valve seat by increasing the flow rate of the refrigerant gas. A refrigerant gas suction amount control device in a rotary compressor.   2. The refrigerant gas suction amount control device for a rotary compressor according to claim 1, wherein the throttle valve including the valve seat and the valve body is unitized.   3. The refrigerant gas intake amount control device for a rotary compressor according to claim 1, wherein the valve seat is formed separately from the intake portion and is attached to the intake portion.   The refrigerant gas intake amount control device for a rotary compressor according to any one of claims 1 to 3, wherein the valve seat and the through hole of the valve body are formed in a perfect circle.   The refrigerant gas suction amount control device for a rotary compressor according to any one of claims 1 to 3, wherein the valve seat and the through hole of the valve body are formed by an ellipse.

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