JP2006046154A - Hermetic compressor and refrigeration cycle apparatus using the same - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a highly reliable hermetic compressor with reduced vibration and noise by reducing the deflection of a shaft by a balancer and preventing the contact of a bearing and the run-out of a rotor.
A low pressure compression element that compresses a fluid from a suction pressure to an intermediate pressure, and a high pressure compression element that compresses a fluid compressed by the low pressure compression element to a discharge pressure. This is achieved by placing the element between the eccentric weight part.
[Selection] Figure 3

Description

  The present invention relates to a hermetic compressor and a refrigeration cycle apparatus using the same.

  2. Description of the Related Art Conventionally, compressors used in refrigeration / air conditioning systems and the like, for example, rotary compressors, have an eccentric weight in a compression element connected to a rotating shaft. In order to cancel the unbalance due to the eccentric weight portion, a balancer is provided on the rotor of the electric element and its peripheral portion. However, there has been a problem that the balancer deflects the rotating shaft, which increases the unbalance and increases the vibration around the bearing piece.

  In order to solve this problem, there is Patent Document 1 (Japanese Patent Laid-Open No. 11-230073) as a prior art for reducing the deflection of the shaft.

  The rotary compressor disclosed in Patent Document 1 includes a compression element that includes a low-stage compression section and a high-stage compression section, and sequentially compresses refrigerant in multiple stages. In this compressor, a rotor balancer is attached to the rotor, and a low-stage compression section with a large excluded volume is arranged in the vicinity of the rotor balancer, and vibration due to eccentricity of each compression section is reduced with a relatively light rotor balancer. To do.

Japanese Patent Laid-Open No. 11-230073

  However, since the deflection of the rotating shaft is proportional to the square of the distance from the shaft support point to the balancer, if a balancer is provided on the upper side of the rotor far from the shaft support point of the main bearing as in the prior art, the shaft will bend easily and vibration will occur. It is conceivable to cause an increase in the number of bearings and contact of the bearing.

  An object of the present invention is to provide a hermetic compressor that reduces the deflection of the shaft, reduces vibration and noise, and is highly reliable by paying attention to the relationship between the balancer and the pivot point. Another object of the present invention is to provide a low-vibration, low-noise refrigeration cycle apparatus using the hermetic compressor of the present invention.

  The above object includes an electric element having a rotation shaft and a compression element driven by the rotation shaft in a sealed container, and the compression element is driven by the rotation shaft and compresses a fluid from a suction pressure to an intermediate pressure. A low-pressure compression element and a high-pressure compression element that compresses the fluid compressed by the low-pressure compression element to a discharge pressure, and at least the low-pressure compression element and the high-pressure compression element are located with respect to the rotating shaft. This is achieved by providing an eccentric weight portion for applying an eccentric force, and one compression element of the low pressure compression element and the high pressure compression element is positioned between the plurality of eccentric weight portions.

  According to the present invention, it is possible to provide a hermetic compressor that can reduce the deflection of the shaft, has low vibration, low noise, and high reliability. In addition, a highly reliable refrigeration cycle apparatus with low vibration and low noise can be provided.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. First, a swing piston type two-stage compressor according to an embodiment of the present invention will be described with reference to FIGS. In this embodiment, the swing piston type will be described, but the present invention can be applied to other types of rotary compressors.

  In FIG. 1, the compression element 1 includes a low-pressure compression element 2 and a high-pressure compression element 3. End plate portions 5 a and 6 a are provided on the main bearing 5 and the sub-bearing 6 that support the drive shaft 4. The end plate portions 5a and 6a and the partition plate 7 close both end openings of the cylinders 2a and 3a of the compression elements. The cylinders 2a and 3a have cylindrical inner peripheral surfaces 2b and 3b (see FIG. 2) inside thereof. The main bearing 5 and the sub-bearing 6 are fixed to the cylinders 2a and 3a so that the rotation shaft of the drive shaft 4 coincides with the central axes of the cylindrical inner peripheral surfaces 2b and 3b of the cylinders 2a and 3a.

  The compression element 1 is directly connected to the electric element 8 via the drive shaft 4. The electric element 8 includes a rotor 9 and a stator 10. The drive shaft 4 is provided with eccentric portions 4a and 4b at portions corresponding to the cylindrical inner peripheral surfaces 2b and 3b of the cylinders 2a and 3a.

  The refrigerant gas enters the cylinder 2a of the low-pressure compression element 2 from the suction pipe 14 of the low-pressure compression element 2 attached to the sealed container 13 through the suction passage 14a and is compressed. The compressed refrigerant gas is discharged from a discharge port 15 formed in the sub-bearing 6, and discharged into the sealed container 13 through the discharge passage 16. Thereafter, the discharged refrigerant gas exits from the discharge pipe 17 and enters the intercooler 18. The refrigerant gas radiated and cooled by the intermediate cooler 18 passes from the suction pipe 19 of the high pressure compression element 3 through the suction passage 19a and enters the cylinder 3a of the high pressure compression element 3 and is compressed. The compressed refrigerant gas is discharged from the discharge port 20 provided in the main bearing 5, and then enters the discharge chamber 21 and flows out from the discharge pipe 22 to the refrigeration cycle provided outside the sealed container 13.

  Next, the compression operation accompanying the rotation of the drive shaft 4 in the compression element will be described with reference to FIG. Since the cylinders 2 and 3 each have a corresponding member, in FIG. 2, one of the symbols is written in parentheses. The description will be made on behalf of the configuration of the cylinder 2.

  The cylindrical inner peripheral surface of the roller portion 2c1 of the swing piston 2c is fitted into the eccentric portion 4a so as to be able to revolve while being in contact with the eccentric portion 4a. The dimensions of each part are determined so that the gap between the cylindrical outer peripheral surface of the roller portion 2c1 and the cylindrical inner peripheral surface 2b of the cylinder 2a is very small. A vane portion 2c2 is provided on the cylindrical outer peripheral surface of the roller portion 2c1. A cylindrical hole 2d having a central axis parallel to the central axis of the cylindrical inner peripheral surface 2b is provided outside the cylindrical inner peripheral surface 2b of the cylinder 2a. The cylinder 2a center side of the cylindrical hole 2d and the opposite side thereof communicate with the cylindrical inner peripheral surface 2b of the cylinder 2a and another hole 2e provided outside the cylindrical hole 2d, respectively.

  The vane portion 2c2 is inserted into the cylindrical hole portion 2d and the hole portion 2e. Between the vane portion 2c2 and the cylindrical hole portion 2d, a flat surface portion that slidably contacts the flat portion of the vane portion 2c2 and a cylindrical surface portion that slidably contacts the cylindrical surface portion of the cylindrical hole portion 2d. And a sliding member 2f having a pinned portion 2c2. As a result, the vane portion 2c2 performs an advancing / retreating motion toward the central axis of the cylindrical hole portion 2d and a swinging motion around the central axis. Specifically, the roller portion 2c1 is oscillated by a slight angle around the central axis of the eccentric portion 4a so that the vane portion 2c2 always faces the central axis direction of the cylindrical hole portion 2d of the cylinder 2a. The tip of any part 2c2 whose center revolves moves in the hole 2e and does not interfere with the cylinder 2a.

  With the above configuration, when the drive shaft 4 is rotated by the electric element 8, the swing piston 2c performs a revolving motion with swing in the cylinder 2a together with the eccentric portion 4a. With respect to sliding of the vane portion 2c2, the vane portion 2c2 performs an advancing / retreating motion toward the central axis of the cylindrical hole portion 2d of the cylinder 2a and a swinging motion around the central axis. The seal between the vane portion 2c2 and the cylindrical hole portion 2d of the cylinder 2a is maintained by inserting the sliding member 2f.

  As described above, the compression chamber which is a sealed space by the cylinders 2a and 3a, the swinging pistons 2c and 3c, the end plates 5a and 6a of the main bearing 5 and the auxiliary bearing 6, the partition plate 7 and the sliding members 2f and 3f. 11 and a suction chamber 12 that is a suction space are configured, and as the drive shaft 4 is rotated by the electric element 8, the volume thereof is repeatedly increased and decreased as shown in FIG.

  Next, the balance action of the rotating system will be described with reference to FIG. When the drive shaft 4 rotates at Nmin-1, the centrifugal force m2 × r2 × N and m3 × r3 × N act on the eccentric weight parts m2 and m3 of the compression element 1, and this compression element with large centrifugal force is the secondary bearing. It is arranged on the support point side. A balancer 23 having an eccentric weight part m1 is fitted to the drive shaft 4 below the auxiliary bearing support point.

These dynamic and static balances are expressed by the following equations (1) and (2).
m1 × r1 + m3 × r3 = m2 × r2 ……… (1)
ml × r1 × L1 + m3 × r3 × L3 = m2 × r2 × L2 ……… (2)
With the above configuration, the unbalance caused by the centrifugal force acting on the eccentric mass m2 and m3 of the compression element 1 is canceled by the balancer 23 provided in the vicinity of the auxiliary bearing support point, so the shaft deflection is small. Further, it is possible to prevent galling due to contact of the bearing pieces. In addition, the run-out of the rotor 9 due to shaft deflection can be reduced, and low vibration and noise can be achieved. Here, the balancer 23 is in the vicinity of the main bearing support point, for example, the lower side of the rotor 9 or the lower side of the auxiliary bearing and the lower side of the rotor 9 as long as the expressions (1) and (2) are satisfied. The same effect can be obtained even if provided.

  Next, another embodiment of the present invention is shown in FIG. In the present embodiment, a compression element having a large centrifugal force acting on the eccentric weight parts m1 and m2 is arranged on the main bearing support point side. On the lower side of the rotor 9, a balancer 24 having an eccentric weight part m3 is installed. These dynamic and static balances are expressed by the above formulas (1) and (2).

  By adopting the above configuration, the unbalance caused by the centrifugal force acting by the eccentric masses m1 and m2 of the compression element 1 is canceled by the balancer 23 provided near the main bearing support point, so that the shaft deflection is small. Further, it is possible to prevent galling due to contact of the bearing pieces. In addition, the swing of the rotor 9 due to the deflection of the shaft can be reduced, and low vibration and noise can be achieved. Here, the balancer 23 is the same even if it is provided below the auxiliary bearing support point and below the rotor 9 and below the auxiliary bearing support point as long as the expressions (1) and (2) are satisfied. The effect is obtained.

  Next, an embodiment when the present invention is applied to a horizontal rotary compressor will be described with reference to FIGS. Here, components having the same reference numerals as those of the above-described embodiment are the same components and perform the same functions. Lubricating oil 24 is stored in the lower part of the hermetic container 13. On the side of the sub-bearing 6 of the drive shaft 4, an oil supply pump 28 including an inner rotor 25 fitted into the eccentric portion 26 and a casing 27 attached to the sub-bearing 6 is provided. The lubricating oil 24 is pumped up to the drive shaft 4 through the oil supply pipe by the oil supply pump 28 and supplied to each bearing sliding portion.

  FIG. 6 shows the balance of the rotating system in this horizontal type. The compression element 1 has an eccentric weight part m2, m3, next to the auxiliary bearing support point, the eccentric weight part m1 of the inner rotor 25 of the oil pump 28, and the rotor 9 has the eccentric weight part m4 of the balancer 23 on the main bearing support point side. There is.

These dynamic and static balances are expressed by equations (3) and (4).
m1 × r1 + m3 × r3 + m4 × r4 = m2 × r2 ……… (3)
m1 x rl x L1 + m3 x r3 x L3 + m4 x r4 x L4 = m2 x r2 x L2 (4)
With the above configuration, the inner rotor 25 of the oil supply pump 28 has the function of the second balancer as well as the oil supply function with respect to the balancer 23 that is the first balancer. Therefore, the balancer 23 can be reduced in weight, and the deflection of the shaft can be reduced.

  Next, a configuration of a refrigeration cycle when a two-stage compressible hermetic compressor to which another embodiment of the present invention is applied is applied to a heat pump type hot water heater will be described with reference to FIG. The refrigerant gas compressed to the intermediate pressure by the low pressure compression element 2 provided in the hermetic compressor 30 to which the embodiment of the present invention is applied is cooled by the intermediate cooler 30a and then discharged by the high pressure compression element 3. Compressed to pressure. The compressed refrigerant gas flowing into the heat exchanger 31 from the discharge pipe 22 exchanges heat with the water in the water passage 32. Thereafter, the refrigerant gas is depressurized by the expansion valve 33, absorbed and gasified by the evaporator 34 that receives the air blown from the evaporator fan 44 a, and then sucked into the hermetic compressor 30 through the suction pipe 14.

  Here, since the heat pump type hot water heater shown in FIG. 9 is equipped with the hermetic compressor of the present invention, a heat pump type hot water heater with low vibration, low noise and high reliability can be obtained.

  As described above, in the embodiment of the present invention, the oscillating piston type compressor is used. However, in the rotary compressor, the same effect can be obtained even when the suction pressure of the low pressure compression element 2 is set in the same hermetic container. In addition to the heat pump device, the present invention can also be applied to a refrigeration air conditioner. In that case, for example, in a separate type room air conditioner, even if rapid cooling or heating is performed by applying a rotary compressor to which the present invention is applied to an outdoor unit, the room air conditioner has low vibration and low noise characteristics. Excellent effects can be obtained.

1 is a longitudinal sectional view of a swinging piston type two-stage compressor according to an embodiment of the present invention. FIG. 2 is an explanatory diagram of a compression operation in which the drive shaft is rotated by 90 ° in the compression element of FIG. FIG. 2 is a balance explanatory diagram of a rotating system of the swing piston type two-stage compressor described in FIG. The balance explanatory view of the rotation system of the swinging piston type two-stage compressor according to another embodiment of the present invention. Fig. 3 is a longitudinal sectional view of a horizontal type oscillating piston type two-stage compressor. FIG. 6 is a balance explanatory diagram of a rotating system of the swing piston type two-stage compressor described in FIG. The figure which shows the heat pump type water heater equipped with the hermetic compressor in the present invention.

Explanation of symbols

1 ... Compression element, 2 ... Low pressure compression element, 2a ... Cylinder, 2b ... Cylindrical inner peripheral surface, 2c ... Oscillating piston, 2c1 ... Roller part, 2c2 vane part, 2d ... Cylindrical hole part, 2e ... Hole Part, 2f ... active member, 3 ... compression element for low pressure, 3a ... cylinder, 3b ... cylindrical inner peripheral surface, 3c ... oscillating piston, 3c1 ... roller part, 3c2 vane part, 3d ... cylindrical hole part, 3e ... hole, 3f ... active member, 4 ... drive shaft, 4a, 4b ... eccentric part, 5 ... main bearing, 6 ... sub-bearing, 7 ... partition plate, 8 ... electric element, 9 / rotor, 10 ... stator , 11 ... Compression chamber, 12 ... Suction chamber, 13 ... Sealed container, 14 ... Suction pipe, 14a ... Suction passage, 15 ... Discharge port, 16 ... Discharge passage, 17 ... Discharge pipe, 18 ... Intermediate cooler, 19 ... Suction Pipe, 19a ... Suction passage, 20 ... Discharge port, 21 / Discharge chamber, 22 ... Discharge pipe, 23 ... Balancer, 24 ... Lubricating oil, 25 ... Inner rotor, 26 ... Eccentric part, 27 ... Casing, 28 ... Oil pump, 29 ... refueling pipe, 30 ... closed type Compressor, 31 ... heat exchanger, 32 ... water passage, 33 ... expansion valve, 34 ... evaporator, 34a ‥ evaporator fan.

Claims (9)

  An electric element having a rotation shaft and a compression element driven by the rotation shaft are provided in a sealed container, and the compression element is driven by the rotation shaft and compresses fluid from a suction pressure to an intermediate pressure. And a high-pressure compression element that compresses the fluid compressed by the low-pressure compression element to a discharge pressure, and at least the low-pressure compression element and the high-pressure compression element have an eccentric force with respect to the rotating shaft. A hermetic compressor in which an eccentric weight portion to be operated is provided, and one compression element of the low pressure compression element and the high pressure compression element is located between a plurality of eccentric weight portions.   A main bearing and a sub-bearing that pivotally support the rotating shaft, and an eccentric weight portion of the compression element on the sub-bearing side includes an eccentric weight portion of the compression element on the main bearing side and an anti-compression element side of the sub-bearing 2. The hermetic compressor according to claim 1, wherein the hermetic compressor is located between an eccentric weight portion provided on the rotary shaft of the compressor.   A main bearing and a sub-bearing that pivotally support the rotating shaft, wherein the eccentric weight portion of the compression element on the main bearing side is the eccentric weight portion of the compression element on the sub-bearing side, and the anti-compression element side of the main bearing 2. The hermetic compressor according to claim 1, wherein the hermetic compressor is located between an eccentric weight portion provided on the rotary shaft of the compressor.   A main bearing and a sub-bearing that pivotally support the rotating shaft, wherein the low-pressure compression element and the high-pressure compression element are the main bearing, and an eccentric weight portion provided on the anti-compression element side of the sub-bearing. 2. The hermetic compressor according to claim 1, which is located between the two.   The hermetic compressor according to claim 3 or 4, wherein the eccentric weight portion is a balancer provided on the main bearing side of the rotor of the electric element.   The hermetic compressor according to claim 3 or 4, wherein the eccentric weight portion is a balancer provided between a rotor of the electric element and the main bearing.   An electric element having a rotation shaft and a compression element driven by the rotation shaft are provided in a sealed container, and the compression element is driven by the rotation shaft and compresses a fluid from a suction pressure to an intermediate pressure. A high pressure compression element that compresses the fluid compressed by the low pressure compression element to a discharge pressure, a main bearing and a sub bearing that pivotally support the rotating shaft, and an oil pump on the side opposite to the compression element of the sub bearing In addition, a first balancer is provided between the rotor of the electric element and the main bearing, the oil pump has an inner rotor coupled to the rotating shaft, and the inner rotor functions as a second balancer. Hermetic type compressor.   The hermetic compressor according to claim 1, wherein the compression element is a rotary type. A refrigeration cycle apparatus equipped with the hermetic compressor according to any one of claims 1 to 8.

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