JP2013036386A - Fluid machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fluid machine that can reduce vibration and noise by keeping the static balance or the dynamic balance with regard to each reciprocating component of at least two or more fluid intake/exhaust mechanisms provided at both end positions on the same drive shaft.SOLUTION: The fluid machine 1 is configured such that two or more fluid intake/exhaust mechanisms 2, 3 are provided at both end positions on the same drive shaft 7 and each of the fluid intake/exhaust mechanisms 2, 3 includes a reciprocating component 36. The reciprocating component 36 of each of the fluid intake/exhaust mechanisms 2, 3 is arranged to be reciprocatingly movable in directions opposite to each other or in the same direction.

Description

  The present invention relates to a fluid machine suitable for application to a compressor, an expander, a pump, or the like in which at least two or more fluid intake / exhaust mechanisms are provided at both end positions on the same drive shaft.

  As a fluid machine in which at least two or more fluid suction / discharge mechanisms are provided at both end positions on the same drive shaft, for example, a compression mechanism of a different type provided at both end positions on the same drive shaft, a compression mechanism at one end side, One provided with an expansion mechanism on the other end side, one provided with a pump mechanism on one end side, one provided with an expansion mechanism on the other end side, and further provided with a low-stage compression mechanism on one end side of the drive shaft and a high-stage compression on the other end side. Various fluid machines such as a two-stage compressor provided with a mechanism are provided.

  As an example of such a fluid machine, for example, Patent Document 1 discloses a two-stage compressor in which a low-stage rotary compression mechanism is provided on the lower end side of the drive shaft and a high-stage scroll compression mechanism is provided on the upper end side. It is disclosed. In this two-stage compressor, the eccentric portion of the crankshaft that drives the rotary compression mechanism and the eccentric pin of the crankshaft that drives the scroll compression mechanism are provided in a direction opposite to each other by 180 ° or in the same direction. The balance of the shaft system, that is, the static balance is mainly provided by providing the eccentric portion and the eccentric pin in the opposing direction, and the dynamic balance is provided mainly by providing the eccentric portion and the eccentric pin in the same direction.

  On the other hand, a multi-cylinder rotary compressor having a plurality of sets of the same compression mechanism generally has a plurality of eccentric portions at one end of a crankshaft as shown in Patent Document 2. By providing this eccentric part in a direction opposite to each other by 180 °, the shaft system of the rotating part is balanced.

JP 2008-175340 A JP 2008-63973 A

  However, as shown in Patent Documents 1 and 2, two or more fluid suction / discharge mechanisms (for example, compression mechanisms) are provided at both end positions on the same drive shaft, and each fluid suction / discharge mechanism includes a reciprocating component. In machinery, the shaft system of the rotating part is normally balanced, but there are some reciprocating parts such as the Oldham ring of the scroll compression mechanism and the blades of the rotary compression mechanism that are balanced. There wasn't. This seems to be because it is difficult to balance the reciprocating parts alone, and this causes the balance of the drive shaft system to become a cause of vibration and noise.

  The present invention has been made in view of such circumstances, and by taking a static balance or a dynamic balance for at least two or more reciprocating parts of the fluid suction / discharge mechanism provided at both end positions on the same drive shaft. An object of the present invention is to provide a fluid machine that can reduce vibration and noise.

In order to solve the above problems, the fluid machine of the present invention employs the following means.
That is, the fluid machine according to the present invention is a fluid machine in which two or more fluid suction / discharge mechanisms are provided at both end positions on the same drive shaft, and each fluid suction / discharge mechanism includes a reciprocating component. The reciprocating parts of the intake / exhaust mechanism are arranged to be able to reciprocate in opposite directions or in the same direction.

  According to the present invention, two or more fluid suction / discharge mechanisms are provided at both end positions on the same drive shaft, and the reciprocating parts of each fluid suction / discharge mechanism are disposed so as to be able to reciprocate in opposite directions or in the same direction. Therefore, when the reciprocating parts are arranged so as to be able to reciprocate in opposite directions, a static balance can be obtained mainly, and the reciprocating parts are arranged so as to be able to reciprocate in the same direction. If you are, you can mainly balance the dynamics. Therefore, by balancing the reciprocating parts of each fluid suction / discharge mechanism, it is possible to prevent the balance of the shaft system from being lost due to the unbalance moment, and to reduce vibration and noise.

  Furthermore, the fluid machine according to the present invention is the above fluid machine, wherein the reciprocating parts of the fluid suction / discharge mechanisms are reciprocally movable in the opposite direction or the same direction with respect to a straight line in the same direction. And a range within ± 45 ° is included.

  According to the present invention, since the reciprocating parts of the fluid suction / discharge mechanisms are capable of reciprocating with each other, the opposite direction or the same direction includes a range within ± 45 ° with respect to a straight line in the direction. The moving parts are not limited to those that can reciprocate in the opposite direction of 180 ° or in the same direction (0 ° direction). The amount of static unbalance or dynamic unbalance can be made sufficiently small by force. Therefore, even when the reciprocating parts cannot be arranged in the opposite direction of 180 ° or in the same direction (0 ° direction), By disposing within the range of ± 45 °, the unbalance moment due to the reciprocating parts can be made as small as possible, and vibration and noise can be reduced.

  Furthermore, the fluid machine according to the first aspect of the present invention is the fluid machine according to any one of the above-described fluid machines, wherein the reciprocating parts of the fluid suction / discharge mechanisms are disposed so as to be capable of reciprocating in opposite directions. When the mass of the first reciprocating part is m1, the stroke is l1, the mass of the second reciprocating part of the second fluid suction / discharge mechanism is m2, and the stroke is l2, m1 × l1≈m2 × l2. It is characterized by.

  According to the present invention, when the reciprocating parts of each fluid suction / discharge mechanism are arranged so as to be reciprocally movable in opposite directions, the mass of the first reciprocating part of the first fluid suction / discharge mechanism is m1 and the stroke is l1. When the mass of the second reciprocating component of the second fluid intake / exhaust mechanism is m2 and the stroke is l2, m1 × l1≈m2 × l2, so that the first reciprocating component of the first fluid intake / exhaust mechanism and the second The imbalance moment due to the second reciprocating component of the two-fluid intake / exhaust mechanism can be substantially canceled out to achieve a dynamic balance. Therefore, it is possible to prevent the balance of the shaft system from being lost due to the unbalance moment caused by the reciprocating parts of each fluid suction / discharge mechanism, and to reliably reduce vibration and noise.

  Furthermore, the fluid machine of the present invention is the fluid machine described above, wherein when the masses m1, m2 of the first and second reciprocating parts are m1> m2, the strokes l1, of the first and second reciprocating parts, When l2 is l1 <l2 and the masses m1 and m2 are m1 <m2, the strokes l1 and l2 are l1> l2.

  According to the present invention, when the masses m1 and m2 of the first and second reciprocating parts are m1> m2, the strokes l1 and l2 of the first and second reciprocating parts are set to l1 <l2, and their masses When m1 and m2 are m1 <m2, since the strokes l1 and l2 are set to l1> l2, the masses m1 and m2 and the strokes l1 and l2 of the first and second reciprocating parts are not necessarily the same. The masses m1 and m2 and the strokes l1 and l2 can be appropriately set to appropriate values. Therefore, the mechanism of the fluid suction / discharge mechanism is different and each reciprocating component can be easily applied to those having different masses and strokes.

  Furthermore, the fluid machine according to the present invention is characterized in that, in any of the fluid machines described above, each of the fluid suction / discharge mechanisms is configured by any one of a compression mechanism, an expansion mechanism, a pump mechanism, or a combination thereof. .

  According to the present invention, each fluid intake / exhaust mechanism is configured by any one of a compression mechanism, an expansion mechanism, a pump mechanism, or a combination thereof, so that the fluid intake / exhaust mechanisms provided at both end positions on the same drive shaft are respectively compressed. By providing mechanisms, expansion mechanisms, pump mechanisms, compression mechanisms and expansion mechanisms, combinations of pump mechanisms and expansion mechanisms, etc., various types of fluid machines are provided, and reciprocating components in each fluid suction and discharge mechanism The static balance or dynamic balance can be achieved. Therefore, by balancing the reciprocating parts of various fluid intake / exhaust mechanisms, it is possible to prevent the balance of the shaft system from being lost due to the unbalance moment, and to reduce vibration and noise.

  Furthermore, the fluid machine according to the present invention is the fluid machine according to any one of the above-described fluid machines, wherein one of the fluid suction / discharge mechanisms is a low-stage compression mechanism and the other fluid suction / discharge mechanism is a high-stage compression mechanism. A two-stage compressor is configured.

  According to the present invention, since one of the fluid intake / exhaust mechanisms is a low-stage compression mechanism and the other one of the fluid intake / exhaust mechanisms is a high-stage compression mechanism, the two-stage compressor is configured. By arranging the reciprocating parts of the low-stage compression mechanism and the high-stage compression mechanism in the compressor so that they can reciprocate in the opposite direction or in the same direction, the low-stage compression mechanism and the high-stage compression mechanism reciprocate. Static balance or dynamic balance of moving parts can be achieved. Therefore, by balancing the reciprocating parts of each compression mechanism, it is possible to prevent the balance of the shaft system from being lost due to the unbalance moment, and to reduce vibration and noise.

  Furthermore, the fluid machine according to the present invention is a scroll fluid suction / discharge mechanism in which one of the fluid suction / discharge mechanisms includes an Oldham ring as the reciprocating component in any of the fluid machines described above. One of these is a rotary fluid suction / discharge mechanism provided with a blade as the reciprocating component.

  According to the present invention, one of the fluid suction and discharge mechanisms is a scroll type fluid suction and discharge mechanism including an Oldham ring as a reciprocating part, and the other one of the fluid suction and discharge mechanisms includes a blade as a reciprocating part. Since it is an intake / exhaust mechanism, the structure of the fluid intake / exhaust mechanism is different. However, by arranging the Oldham ring and the blade so that they can reciprocate in the opposite direction or in the same direction, the reciprocating parts of the scroll type fluid intake / exhaust mechanism and the rotary type fluid intake / exhaust mechanism can be statically balanced or dynamically balanced. Can do. Therefore, it is possible to prevent the balance of the shaft system from being lost due to the unbalance moment caused by the reciprocating parts of the fluid suction / discharge mechanisms having different configurations, and to reduce vibration and noise. When comparing the Oldham ring and the blade, the size of the parts is different, but the stroke is different, and the mass can be made different by changing the material, so that the static balance or the dynamic balance can be sufficiently balanced.

  Furthermore, in the fluid machine according to the present invention, in the fluid machine described above, the rotary fluid suction / discharge mechanism is a two-cylinder rotary fluid suction / discharge mechanism, and the two blades are disposed so as to reciprocate in opposite directions. In addition, the blade on the side close to the scroll fluid suction / discharge mechanism is disposed so as to be capable of reciprocating in a direction opposite to the Oldham ring of the scroll fluid suction / discharge mechanism.

  According to the present invention, the rotary fluid suction / discharge mechanism is a two-cylinder rotary fluid suction / discharge mechanism, and the two blades are disposed so as to be able to reciprocate in opposite directions and are close to the scroll fluid suction / discharge mechanism. Since the blade on the side is arranged so as to be able to reciprocate in the opposite direction to the Oldham ring of the scroll type fluid intake / exhaust mechanism, the rotary type fluid intake / exhaust mechanism is advantageous for the capacity and torque fluctuation of the rotary type fluid intake / exhaust mechanism Even when a two-cylinder rotary type fluid intake / exhaust mechanism is used, a static balance can be achieved by arranging the two blades so as to be capable of reciprocating in opposite directions. In this case, the static unbalance due to the Oldham ring on the scroll fluid suction / discharge mechanism side remains, but by adjusting the phase in the reciprocating direction of the blade on the side far from the Oldham ring and the scroll fluid suction / discharge mechanism, the dynamic unbalance amount is reduced. Can be small. Therefore, the amount of dynamic unbalance due to the reciprocating parts can be reduced, and the shaft system balance can be secured.

  Furthermore, the fluid machine according to the present invention is the fluid machine according to any one of the above-described fluid machines, wherein the blade on the side close to the scroll fluid suction / discharge mechanism of the two-cylinder rotary fluid suction / discharge mechanism is on the side far from the scroll fluid suction / discharge mechanism. The weight is made heavier than that of the blade or the stroke is made longer.

  According to the present invention, the blade on the side close to the scroll fluid suction / discharge mechanism of the two-cylinder rotary fluid suction / discharge mechanism is heavier than the blade farther from the scroll fluid suction / discharge mechanism or has a longer stroke. Therefore, the static balance between the two blades of the two-cylinder rotary type fluid intake / exhaust mechanism cannot be achieved and the static unbalance remains, but by making this face the static balance by the Oldham ring on the scroll type fluid intake / exhaust mechanism side, The amount of dynamic imbalance can be minimized. As a result, the amount of dynamic unbalance due to the reciprocating parts can be made as small as possible, and the shaft system balance can be secured.

  According to the present invention, when the reciprocating parts of two or more fluid intake / exhaust mechanisms provided at both end positions on the same drive shaft are arranged so as to be reciprocable in opposite directions, a static balance can be mainly achieved. In addition, when the reciprocating parts are arranged so that they can reciprocate in the same direction, it is possible to balance the movement mainly. Therefore, by balancing the reciprocating parts of each fluid suction and discharge mechanism, It is possible to prevent the balance of the shaft system from being lost due to the balance moment, and to reduce vibration and noise.

1 is a longitudinal sectional view of a fluid machine (two-stage compressor) according to a first embodiment of the present invention. It is an AA cross-section equivalent figure in FIG. It is a BB cross-section equivalent figure in FIG. It is a schematic diagram of the fluid machine (two-stage compressor) which concerns on 2nd Embodiment of this invention. It is a schematic diagram of the comparative example with respect to 2nd Embodiment of FIG. It is a graph which shows the relationship between the phase of a blade motion direction with respect to the Oldham ring motion direction of the fluid machine which concerns on 1st Embodiment of FIG. 1, and the amount of static unbalances. It is a graph which shows the relationship between the phase of an upper blade motion direction with respect to the Oldham ring motion direction of a fluid machine which concerns on 2nd Embodiment of FIG. 4, and a dynamic imbalance amount.

Embodiments according to the present invention will be described below with reference to the drawings.
[First Embodiment]
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 to 3 and FIG. 6.
FIG. 1 is a longitudinal sectional view of a fluid machine according to the first embodiment of the present invention, FIG. 2 is an equivalent view taken along the line AA, and FIG. 3 is an equivalent view taken along the line BB. It is shown. In the present embodiment, for the sake of convenience, as an example of a fluid machine in which at least two fluid suction / discharge mechanisms are connected to both end positions on the same drive shaft, a low-stage compression mechanism that is one fluid suction / discharge mechanism is used. An example of a two-stage compressor 1 that uses a scroll-type compression mechanism 3 as a rotary-type compression mechanism 2 and a high-stage side compression mechanism, which is another fluid intake / exhaust mechanism, will be described. Of course, the invention is not limited to such a two-stage compressor 1.

  A two-stage compressor (fluid machine) 1 according to the present embodiment includes a hermetically sealed housing 10. A motor 4 including a stator 5 and a rotor 6 is fixedly installed at a substantially central portion in the hermetic housing 10, and a drive shaft (crank shaft) 7 is integrally coupled to the rotor 6. A low-stage rotary compression mechanism 2, which is one fluid intake / exhaust mechanism, is provided at a position below the motor 4 on one end side of the drive shaft 7.

  The low-stage rotary compression mechanism 2 includes a cylinder chamber 20. The cylinder body 21 is fixedly installed in the hermetic housing 10 at a plurality of locations by plug welding or the like, and is fixedly installed above and below the cylinder body 21. An upper bearing 22 and a lower bearing 23 that seal the upper and lower portions, a rotor 24 that is fitted to the crank portion 7A of the drive shaft 7 and rotates on the inner peripheral surface of the cylinder chamber 20, and the inside of the cylinder chamber 20 as the suction side A blade 25 that partitions the discharge side and a blade pressing spring 26 (see FIG. 3) that presses the blade 25 are provided.

  The low-stage rotary compression mechanism 2 itself may be a known one, and sucks low-pressure refrigerant gas (working gas) into the cylinder chamber 20 through the suction pipe 27 and rotates the rotor 24 with the refrigerant gas. After being compressed to an intermediate pressure, the pressure is discharged into the discharge chambers 28A and 28B, merged in the discharge chamber 28A, and then discharged into the sealed housing 10. This intermediate-pressure refrigerant gas flows through the gas passage hole 6A provided in the rotor 6 of the motor 4 and flows into the space above the motor 4 to the high-stage scroll compression mechanism 3 that is a fluid intake / exhaust mechanism. It is inhaled and compressed in two stages.

  The high-stage scroll compression mechanism 3, which is another fluid intake / exhaust mechanism, is provided on the other end side of the drive shaft 7 and above the motor 4, and a bearing 30 that supports the drive shaft 7 is provided. , And is mounted on a support member 31 (also called a frame member or a bearing member) fixedly installed in the hermetic housing 10. The support member 31 is fixedly installed at a plurality of locations on the circumference with respect to the sealed housing 10 by plug welding or the like, and a refrigerant gas suction flow between the outer peripheral surface and the inner peripheral surface of the sealed housing 10 is provided. A notch 31A (see FIG. 2) constituting the path is formed.

  The high-stage scroll compression mechanism 3 includes spiral wraps 32B and 33B standing on end plates 32A and 33A, respectively, and the spiral wraps 32B and 33B are engaged with each other and assembled on the support member 31. By connecting the fixed scroll member 32 and the orbiting scroll member 33 constituting the pair of compression chambers 34, the orbiting scroll member 33 and the eccentric pin 7B provided at the shaft end of the drive shaft 7, the orbiting scroll member 33 is revolved. A rotating boss portion 35 to be driven, an Oldham ring 36 provided between the orbiting scroll member 33 and the support member 31 as a rotation preventing mechanism for revolving while preventing the rotation of the orbiting scroll member 33, and the back surface of the fixed scroll member 32 The fixed valve is provided on the back side of the discharge valve 40 and the fixed scroll member 32 provided in the fixed scroll portion. And a discharge cover 42 or the like for forming the discharge chamber 41 between the 32.

  The high-stage scroll compression mechanism 3 itself may be a known one, and the intermediate-pressure refrigerant gas compressed by the low-stage rotary compression mechanism 2 and discharged into the sealed housing 10 is sucked into the compression chamber 34. After being compressed to the discharge pressure (high pressure) by the revolving orbiting drive of the orbiting scroll member 33, it is configured to be discharged to the discharge chamber 41 through the discharge valve 40. The high-pressure refrigerant gas is discharged from the discharge chamber 41 through the discharge pipe 43 to the outside of the compressor, that is, to the refrigeration cycle side.

  A known positive displacement oil pump 11 is incorporated between the lowermost end portion of the drive shaft 7 and the lower bearing 23 of the low-stage rotary compression mechanism 2. The oil pump 11 is provided in the drive shaft 7 by pumping up lubricating oil (hereinafter also referred to simply as oil) 13 filled in an oil reservoir 12 formed at the bottom of the hermetic housing 10. The lubricating oil 13 is forcibly supplied to a required lubricating portion such as a bearing portion of the low-stage rotary compression mechanism 2 and the high-stage scroll compression mechanism 3 through the oil supply hole 14.

  Further, the high-stage scroll compression mechanism 3 is provided with an oil discharge path for returning the lubricating oil that has lubricated a required lubricating portion such as a bearing portion to the oil reservoir 12 at the bottom of the sealed housing 10. This oil drainage path is formed between the space 44 of the support member 31 and the outer periphery of the support member 31 in which the rotating boss portion 35 of the orbiting scroll member 33 is accommodated and the oil that has lubricated the required lubrication site is collected. The oil drain hole 45 and the oil drain pipe 47 inserted and installed in the downward pipe insertion hole 46 intersecting the oil drain hole 45 are configured. The oil drain pipe 47 extends downward from the lower surface of the support member 31, and its lower end is positioned below the stator coil end 5 </ b> A of the motor 4 and faces one of the stator cuts 5 </ b> B provided on the outer periphery of the stator 5. Is open.

  In the two-stage compressor 1, the eccentric portion 7A of the drive shaft 7 that drives the low-stage rotary compression mechanism 2 that is the first fluid suction / discharge mechanism, and the high-stage scroll compression mechanism that is the second fluid suction / discharge mechanism. The eccentric pin 7B of the drive shaft 7 that drives the motor 3 is provided in the opposite direction or in the same direction. As a result, the axial balance of the rotating parts of the compression mechanisms 2 and 3, that is, by providing the eccentric part 7 </ b> A and the eccentric pin 7 </ b> B in the opposing direction, a static balance is mainly obtained, and the eccentric part 7 </ b> A and the eccentric pin 7 </ b> B are identical. By providing in the direction, it is mainly configured to balance the dynamics.

  Further, in the high stage side scroll compression mechanism (second fluid suction / discharge mechanism) 3, the Oldham ring 36 for preventing the rotation of the orbiting scroll member 33 is compared with the elliptical ring portion 36A as shown in FIG. A pair of keys 36B and 36C are provided on the front side and the back side in the cross direction, and the key 36B on the front side is provided with a key groove (on the back side of the end plate 33A of the orbiting scroll member 33). The key 36C on the back surface side is slidably fitted in a key groove 31B provided on the thrust bearing surface of the support member 31. The Oldham ring (second reciprocating part) 36 is disposed so as to reciprocate on a straight line S shown in FIG. 2 passing through the center of the key groove 31B.

  On the other hand, in the low-stage rotary compression mechanism (first fluid intake / exhaust mechanism) 2, the blade 25 that divides the inside of the cylinder chamber 20 into a suction side and a discharge side, as shown in FIG. In the blade groove 21 </ b> A provided in the radial direction, a front end portion is slidably fitted via a blade pressing spring 26 so as to protrude into the cylinder chamber 20. The blade (first reciprocating component) 25 is most preferably disposed so as to be capable of reciprocating in 180 ° opposite direction to the Oldham ring 36, but is not necessarily limited to the direction opposing 180 °. In consideration of the magnitude of the component force, a range within ± 45 ° with respect to the straight line S in a direction opposite to 180 ° is included.

  In the present embodiment, the blade 25 is disposed so as to be able to reciprocate on a straight line R inclined by 20 ° with respect to a straight line S on which the Oldham ring 36 reciprocates. As described above, the reciprocating direction of the blade 25 is most preferably 180 ° opposite to the Oldham ring 36, but the maximum allowable range is within ± 45 °, preferably within ± 30 °. More preferably, the range is within ± 20 °.

Further, the blade (first reciprocating part) 25 of the low-stage side rotary compression mechanism (first fluid suction / discharge mechanism) 2 and the Oldham ring (first stage) of the high-stage side scroll compression mechanism (second fluid suction / discharge mechanism) 3 are used. 2 reciprocating parts) 36, the mass of the blade (first reciprocating part) 25 is m1, the stroke when reciprocating is l1, the mass of the Oldham ring (second reciprocating part) 36 is m2, the stroke when reciprocating Is set to l2, the following equation (1) is satisfied.
m1 × l1 ≒ m2 × l2 (1)

  In general, due to the size, material, etc. of the above two parts, when each of the masses m1 and m2 is m1> m2, the strokes l1 and l2 are set to l1 <l2 and the above equation (1) is satisfied, When m1 and m2 are m1 <m2, the above formula (1) may be satisfied by setting the strokes l1 and l2 to be l1> l2. In this embodiment, the Oldham ring (second reciprocating part) 36 is considerably larger than the blade (first reciprocating part) 25, and m2> m1, while the stroke during the reciprocating movement is l2 <l1. However, since it is difficult to satisfy the formula (1) if the same material is used because the sizes are very different, the Oldham ring (first reciprocating part) 36 should be made of a lightweight aluminum alloy material. Therefore, it is configured to satisfy the above equation (1).

  In this embodiment, the blade 25 that is the reciprocating component of the low-stage-side rotary compression mechanism 2 and the Oldham ring 36 that is the reciprocating component of the high-stage-side scroll-type compression mechanism 3 are reciprocated in opposite directions. The blade 25 and the Oldham ring 36 which are reciprocating parts are mainly arranged to be statically balanced by being arranged so as to be movable. However, the blade 25 and the Oldham ring 36 are arranged in the same direction (0 ° direction and The blade 25 and the Oldham ring 36 which are the reciprocating parts may be mainly balanced in movement by disposing the reciprocating parts within a range of ± 45 ° with respect to that direction.

With the configuration described above, according to the present embodiment, the following operational effects can be obtained.
The low-pressure refrigerant gas sucked into the cylinder chamber 20 of the low-stage-side rotary compression mechanism 2 through the suction pipe 27 is compressed to the intermediate pressure by the rotation of the rotor 24 and then discharged to the discharge chambers 28A and 28B. The intermediate pressure refrigerant gas is merged in the discharge chamber 28 </ b> A and discharged into the lower space of the electric motor 4, and then flows through the gas passage hole 6 </ b> A provided in the rotor 6 of the motor 4 and the upper portion of the motor 4. Flowed into space.

  The intermediate-pressure refrigerant gas that has flowed into the upper space of the motor 4 passes through a notch 31A provided on the outer peripheral surface of the support member 31 that constitutes the high-stage scroll compression mechanism 3, and thus the high-stage scroll compression mechanism. 3 and is sucked into the compression chamber 34. This intermediate-pressure refrigerant gas is compressed in two stages to a high pressure by the high-stage scroll compression mechanism 3, and then discharged from the discharge valve 40 into the discharge chamber 41. It is sent to the cycle side.

  During the two-stage compression process, the oil 13 supplied to the lubrication part of the low-stage rotary compression mechanism 2 through the oil supply hole 14 in the drive shaft 7 by the oil supply pump 11 is sealed after lubricating the required part. It flows down to the oil sump 12 at the bottom of the housing 10. Further, the oil 13 supplied to the lubrication part of the high-stage scroll compression mechanism 3 is partly dissolved in the refrigerant gas after lubricating the required part, and is sent to the refrigeration cycle side together with the discharge gas. The portion is collected in the space 44 and is guided through the oil drain hole 45 and the oil drain pipe 47 into the stator cut 5B of the motor 4 from the lower end opening of the oil drain pipe 48, and the sealed housing through the stator cut 5B. The oil will flow down to the oil sump 12 at the bottom of 10.

  Further, the rotating portion of the low-stage rotary compression mechanism 2 and the rotating portion of the high-stage scroll compression mechanism 3 which are connected to both end positions of the drive shaft 7 and are driven by the rotation of the drive shaft 7 are respectively low. By providing the eccentric portion 7A and the eccentric pin 7B of the drive shaft 7 coupled to the stage side rotary compression mechanism 2 and the high stage side scroll compression mechanism 3 in the opposite direction or the same direction, the static unbalance amount Alternatively, the amount of dynamic unbalance is reduced, and the shaft system balance of the drive shaft 7 is taken, so that vibration and noise are reduced.

  Similarly, in this embodiment, reciprocation between the blade 25 which is a reciprocating part of the low-stage rotary compression mechanism 2 which is the first fluid suction / discharge mechanism and the high-stage scroll compression mechanism 3 which is the second fluid suction / discharge mechanism. The Oldham ring 36, which is a moving part, is disposed so as to be able to reciprocate in the opposite direction or in the same direction. The amount of balance can be made as small as possible.

  Thus, according to the present embodiment, only the axial balance of the rotating parts of the low-stage rotary compression mechanism 2 that is the first fluid intake / exhaust mechanism and the high-stage scroll compression mechanism 3 that is the second fluid intake / exhaust mechanism. In addition, it is possible to balance the reciprocating parts such as the blade 25 and the Oldham ring 36 provided in the respective compression mechanisms 2 and 3, and accordingly, the unbalance moment caused by the reciprocating parts 25 and 36. It is possible to prevent the balance of the shaft system from being lost and reliably reduce vibration and noise.

The graph of FIG. 6 shows the relationship between the phase [deg] of the movement direction of the blade 25 relative to the movement direction of the Oldham ring 36 and the static unbalance amount [g ^* mm]. From this graph, it is clear that the static unbalance amount is minimized by arranging the Oldham ring 36 and the blade 25 so as to be reciprocally movable in directions opposite to each other by 180 °. Note that the curves x and y in the graph of FIG. 6 are lines representing changes in the amount of static unbalance in the x and y directions passing through the center of the drive shaft 7, and the curve R is the total line and the phase is 180. At [deg], it can be seen that the static unbalance amount [g ^* mm] is a minimum.

  Further, the opposing direction or the same direction in which the reciprocating parts such as the blade 25 and the Oldham ring 36 can reciprocate includes a range within ± 45 ° with respect to a straight line in the direction. Therefore, the blade 25 and the Oldham ring 36 are not limited to be disposed so as to be capable of reciprocating in the opposite direction to each other or in the same direction (0 ° direction), but within ± 45 ° with respect to each direction. If arranged, the amount of static unbalance or dynamic unbalance can be made sufficiently small by the component force, so that the blade 25 and the Oldham ring 36 are opposed to each other by 180 ° or in the same direction (0 ° direction). Even if it is not possible to arrange in the direction, by placing it within the range of ± 45 ° with respect to each direction, the unbalance moment due to the reciprocating parts is minimized, and vibration and noise are reduced can do.

  Furthermore, in this embodiment, the blade (first reciprocating component) 25 of the low-stage rotary compression mechanism (first fluid intake / exhaust mechanism) 2 that can reciprocate in opposite directions, and the high-stage scroll type. The Oldham ring (second reciprocating part) 36 of the compression mechanism (second fluid intake / exhaust mechanism) 3 has a mass of the blade (first reciprocating part) 25 m1, a stroke of 11, and an Oldham ring (second reciprocating part). When the mass of 36 is m2 and the stroke is l2, m1 × l1≈m2 × l2. Therefore, the unbalance moment caused by the blade (first reciprocating component) 25 and the Oldham ring (second reciprocating component) 36 can be substantially cancelled, and a dynamic balance can be achieved. Therefore, the reciprocating component 25 of each compression mechanism. , 36 can prevent the balance of the shaft system from being lost due to the unbalance moment, and can reliably reduce vibration and noise.

  In the above description, when the masses m1 and m2 of the blade (first reciprocating component) 25 and the Oldham ring (second reciprocating component) 36 are m1> m2, the respective strokes l1 and l2 are l1 <l2. When the masses m1 and m2 are m1 <m2, the strokes l1 and l2 are set to l1> l2. Therefore, the blade (first reciprocating part) 25 and the Oldham ring (second reciprocating part) The masses m1 and m2 and the strokes l1 and l2 of 36 are not necessarily the same, and the masses m1 and m2 and the strokes l1 and l2 can be appropriately set to appropriate values. Therefore, the mechanism of the compression mechanism (fluid suction / discharge mechanism) is different, and each reciprocating component can be easily applied to those having different masses and strokes.

  In the present embodiment, one of the fluid suction / discharge mechanisms is a low-stage rotary compression mechanism 2 and the other fluid suction / discharge mechanism is a high-stage scroll compression mechanism 3, each of which is a reciprocating component blade 25. And the Oldham ring 36 is provided and the two-stage compressor 1 is comprised. The blade 25 and the Oldham ring 36 which are the reciprocating parts are disposed so as to be reciprocally movable in the opposite direction or the same direction, so that the low-stage rotary fluid suction / discharge mechanism 2 and the high-stage scroll compression mechanism A static balance or a dynamic balance of the blade 25 and the Oldham ring 36 which are the three reciprocating parts is obtained.

  As a result, it is possible to prevent the balance of the shaft system from being lost due to the unbalanced moment caused by the reciprocating parts 25 and 36 of the two fluid intake / exhaust mechanisms having different configurations (the low-stage rotary compression mechanism 2 and the high-stage scroll compression mechanism 3). In addition, vibration and noise can be reduced. When comparing the blade 25 and the Oldham ring 36, the Oldham ring 36 is considerably larger in size, and the strokes l1 and l2 during the reciprocating motion are slightly larger in the blade 25 and are different from each other. , By changing the material and making the masses m1 and m2 different, the static balance or the dynamic balance can be sufficiently balanced, and vibration and noise can be reduced.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIGS. 4, 5 and 7.
This embodiment differs from the first embodiment described above in that the low-stage rotary compression mechanism is a two-cylinder rotary compression mechanism 2A. Since other points are the same as those in the first embodiment, description thereof will be omitted.
In the present embodiment, the low-stage rotary compression mechanism is a two-cylinder rotary compression mechanism 2 </ b> A in order to cope with the capacity and torque fluctuation of the rotary compression mechanism, and is eccentric with respect to the lower end portion of the drive shaft 7. Two cylinder chambers 20 are formed in the cylinder body 21 corresponding to the two upper and lower portions 7A, and the rotor 24 can be rotated by the eccentric portion 7A of the drive shaft 7 in each cylinder chamber 20. It is set as the provided structure.

  In the two-cylinder rotary compression mechanism 2A, as shown in FIG. 4, two blades 25A and 25B are vertically arranged corresponding to each cylinder chamber 20 so as to be capable of reciprocating in the radial direction. The two upper and lower blades 25A and 25B and the two upper and lower eccentric portions 7A are arranged in directions opposite to each other by 180 °, and are respectively a rotating portion and a reciprocating component in the two-cylinder rotary compression mechanism 2A. The blades 25A and 25B are configured to be statically balanced.

  Here, the low-stage-side rotary compression mechanism that is one of the fluid suction and discharge mechanisms is a two-cylinder rotary compression mechanism 2A, and in the two-cylinder rotary compression mechanism 2A, the rotating part and the blades 25A that are reciprocating parts are provided. When the static balance of 25B is taken, the static balance of the Oldham ring 36 of the high stage side scroll type compression mechanism 3 which is the other fluid intake-exhaust mechanism will remain. Therefore, as shown in FIG. 4, the reciprocating direction of the Oldham ring 36 and the lower blade 25B of the two-cylinder rotary compression mechanism 2A, that is, the blade 25B far from the high-stage scroll compression mechanism 3, is the same. The upper blade 25A is arranged so as to be able to reciprocate in the opposite direction to the Oldham ring 36.

  That is, when one of the fluid intake / exhaust mechanisms is the two-cylinder rotary compression mechanism 2A, the two-cylinder rotary compression mechanism 2A as shown in FIG. As shown in FIG. 4, the reciprocating direction of the upper blade 25 </ b> A, that is, the blade 25 </ b> A close to the high-stage scroll compression mechanism 3 is arranged in phase with the same direction. It is conceivable that the upper blade 25A, that is, the reciprocating direction of the blade 25A on the side close to the high-stage scroll compression mechanism 3, is arranged as the opposing direction. In this embodiment, the latter configuration is considered. Is adopted.

  Thus, even when one of the fluid intake / exhaust mechanisms is a two-cylinder rotary compression mechanism 2A, the upper and lower two blades 25A and 25B, which are the reciprocating parts, are disposed so as to be reciprocally movable in opposite directions. It is possible to achieve a static balance in the 2-cylinder rotary compression mechanism 2A. In this case, static unbalance remains due to the Oldham ring 36 which is a reciprocating component on the high-stage scroll compression mechanism 3 side, but the blade 25B on the side far from the Oldham ring 36 and the high-stage scroll compression mechanism 3 remains. By matching the phases in the reciprocating direction, the unbalance moment due to the reciprocating parts acting on the axial center of the drive shaft 7 can be canceled, and the amount of dynamic unbalance can be minimized. As a result, the amount of dynamic unbalance due to the reciprocating parts can be reduced, and the shaft system balance can be secured.

The graph of FIG. 7 illustrates the relationship between the phase [deg] of the movement direction of the two blades 25A and 25B with respect to the movement direction of the Oldham ring 36 and the dynamic unbalance amount [g ^* mm2]. Also from this graph, the Oldham ring 36 and the upper blade 25A are arranged so that they can reciprocate in directions opposite to each other by 180 ° (the Oldham ring 36 and the lower blade 25B are in the same phase direction). Obviously it is minimized. Note that curves x and y in the graph of FIG. 7 are lines representing changes in the dynamic unbalance amount in the x and y directions passing through the center of the drive shaft 7, and a curve R is the total line and the phase is 180. It can be seen that the dynamic unbalance amount [g ^* mm2] is a minimum when [deg].

  Further, in the present embodiment, the upper blade 25A close to the high-stage scroll compression mechanism 3 in the two-cylinder rotary compression mechanism 2A is set to be lower than the lower blade 25B far from the high-stage scroll compression mechanism 3. The mass can be increased or the stroke can be increased. With this configuration, even if the static balance between the two upper and lower blades 25A and 25B cannot be achieved in the two-cylinder rotary compression mechanism 2A and a static unbalance remains, The amount of dynamic unbalance can be minimized by facing the static balance by the Oldham ring 36. Therefore, this also makes it possible to reduce the amount of dynamic unbalance of the reciprocating parts as much as possible and to ensure the balance of the shaft system.

  In addition, this invention is not limited to the invention concerning the said embodiment, In the range which does not deviate from the summary, it can change suitably. For example, in the above-described embodiment, an example in which the fluid suction / discharge mechanism is applied to the two-stage compressor 1 having a compression mechanism has been described. However, in addition to the compression mechanism, an expansion mechanism, a pump mechanism, or a combination thereof is used, and a drive shaft The fluid suction / discharge mechanism provided at both end positions of the compressor 7 is composed of compression mechanisms, expansion mechanisms, pump mechanisms, a compression mechanism and an expansion mechanism, a combination of a pump mechanism and an expansion mechanism, and the like. By providing static balance or dynamic balance of reciprocating parts in each fluid suction / discharge mechanism, it is possible to prevent the shaft system balance from being lost due to the unbalance moment, and to reduce vibration and noise. .

1 Two-stage compressor (fluid machine)
2 Low stage rotary compression mechanism (first fluid suction / discharge mechanism)
2A 2-cylinder rotary compression mechanism (first fluid suction / discharge mechanism)
3 High-stage scroll type compression mechanism (second fluid suction / discharge mechanism)
7 Drive shaft 25, 25A, 25B Blade (first reciprocating part)
36 Oldham ring (second reciprocating part)

Claims (9)

Two or more fluid suction / discharge mechanisms are provided at both end positions on the same drive shaft, and each fluid suction / discharge mechanism includes a reciprocating component;
The fluid machine according to claim 1, wherein the reciprocating parts of the fluid suction / discharge mechanisms are arranged to be reciprocally movable in opposite directions or in the same direction.   The range in which the reciprocating parts of the fluid suction / discharge mechanisms are allowed to reciprocate is within a range of ± 45 ° with respect to a straight line in the direction. Item 2. The fluid machine according to Item 1. When the reciprocating parts of the fluid suction / discharge mechanisms are disposed so as to be able to reciprocate in opposite directions, the mass of the first reciprocating part of the first fluid suction / discharge mechanism is m1, the stroke is l1, and the second fluid When the mass of the second reciprocating part of the intake / exhaust mechanism is m2 and the stroke is l2,
m1 × l1 ≒ m2 × l2
The fluid machine according to claim 1, wherein the fluid machine is configured as follows.   When the masses m1 and m2 of the first and second reciprocating parts are m1> m2, the strokes l1 and l2 of the first and second reciprocating parts are set to l1 <l2, and the masses m1 and m2 are 4. The fluid machine according to claim 3, wherein the strokes l 1 and l 2 satisfy l 1> l 2 when m 1 <m 2.   5. The fluid machine according to claim 1, wherein each of the fluid intake / exhaust mechanisms is configured by any one of a compression mechanism, an expansion mechanism, and a pump mechanism, or a combination thereof.   2. A two-stage compressor is constructed by using one of the fluid suction / discharge mechanisms as a low-stage compression mechanism and the other of the fluid suction / discharge mechanisms as a high-stage compression mechanism. Thru | or 5. The fluid machine in any one of 5.   One of the fluid intake / exhaust mechanisms is a scroll type fluid intake / exhaust mechanism including an Oldham ring as the reciprocating part, and the other one of the fluid intake / exhaust mechanisms includes a blade as the reciprocating part. The fluid machine according to claim 1, wherein the fluid machine is configured as follows.   The rotary fluid suction / discharge mechanism is a two-cylinder rotary fluid suction / discharge mechanism, and the two blades are disposed so as to be able to reciprocate in opposite directions, and a blade on the side close to the scroll fluid suction / discharge mechanism is provided. The fluid machine according to claim 7, wherein the fluid machine is disposed so as to be capable of reciprocating in a direction opposite to the Oldham ring of the scroll type fluid suction / discharge mechanism. The blade closer to the scroll fluid suction / discharge mechanism of the two-cylinder rotary fluid suction / discharge mechanism is heavier than the blade farther from the scroll fluid suction / discharge mechanism, or has a longer stroke. The fluid machine according to claim 8, wherein:

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