JP2007211716A - Turbo compressor and freezer equipped with turbo compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a turbo compressor capable of enhancing stability of operation for moving a diffuser ring partitioning a diffuser flow passage to an axial direction. <P>SOLUTION: The turbo compressor is provided with the diffuser ring 33, a support structure body 35 fixed by a housing of the turbo compressor and supporting the diffuser ring 33 so as to be capable of being movable along the axial direction, a plurality of rocking members 37 disposed in the support structure body 35 so as to have a space from the diffuser ring 33 along a peripheral direction and capable of being rocked with respect to the support structure body 35, a connection member 39 connecting the respective rocking members 37 and the diffuser ring 33 and converting the rocking movement of the rocking member 37 to the linear movement in the axial direction so that the diffuser ring 33 is moved to the axial direction when the respective rocking members 37 are rocked, a driving mechanism 34 for giving the rocking force to the plurality of the rocking members 37, and a transmission means 43 for transmitting the rocking force from the driving mechanism 34 to the rocking member 37 so that the plurality of the rocking members 37 are synchronously rocked. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a turbo compressor and a refrigerator including the turbo compressor.

The refrigerator is a so-called heat pump that operates using liquefied gas as a refrigerant and spends work to transfer heat from a low heat source to a high heat source.
A refrigerator usually includes a turbo compressor, a condenser, an expansion valve, and an evaporator. The refrigerant gas is compressed by the compressor to a high temperature and high pressure state, and the refrigerant gas in this state is radiated and liquefied by the condenser. Then, this liquid is expanded by an expansion valve to be in a low-temperature and low-pressure gas-liquid mixed state, and heat is taken away by the medium to be cooled by the evaporator to form a refrigerant gas, which is again sucked into the compressor.

  Refrigerators equipped with a turbo compressor include single-stage turbo chillers and multi-stage turbo chillers. The single-stage turbo refrigerator is a turbo compressor having a single-stage impeller that boosts the refrigerant gas in a single stage, a condenser that condenses and liquefies the refrigerant that has been boosted by the turbo compressor, and depressurizes the refrigerant liquefied in the condenser. An expansion valve and an evaporator for evaporating and evaporating the refrigerant decompressed by the expansion valve are provided.

On the other hand, the multi-stage turbo chiller, taking a two-stage turbo chiller as an example, a turbo compressor having a two-stage impeller that boosts refrigerant gas in two stages, and a condenser that condenses and liquefies the refrigerant boosted by the turbo compressor And an intermediate cooler having two expansion valves that depressurize the refrigerant liquefied in the condenser in two stages, and an evaporator that evaporates and evaporates the refrigerant depressurized by each expansion valve.
In the intercooler, the refrigerant liquefied by the condenser is temporarily stored and cooled, and the gas phase component in the intercooler is supplied to the second stage impeller of the turbo compressor through the bypass pipe. It has become so.

In the configuration of the single-stage or multi-stage refrigerator as described above, cold water cooled by heat exchange with the refrigerant in the evaporator is used for cooling.
In the following, a multi-stage turbo chiller will be described as an example, but the present invention is not limited to a multi-stage turbo chiller, but can be applied to a single-stage turbo chiller.

Such a turbo compressor of a two-stage turbo refrigerator is described in Patent Document 1 below, for example.
FIG. 11 shows the configuration of the turbo compressor disclosed in Patent Document 1. As shown in FIG. 11, the turbo compressor includes a rotating shaft 55 on which two-stage impellers 51 and 52 arranged at intervals in the axial direction are fixed, and a motor 57 (for example, for rotating the rotating shaft). , Induction motor).
A large gear 58a and a small gear 55a that are engaged with each other and transmit the rotational force of the motor to the rotation shaft are fixed to the output shaft 58 and the rotation shaft 55 of the motor 57, respectively.

  When the rotating shaft 55 is rotationally driven by the motor, the speed and pressure of the refrigerant sucked from the suction port 59 to the first impeller 51 are increased by the action of the first impeller 51. This refrigerant is guided from the inside in the radial direction to the outside by the first diffuser channel 63 extending from the inside in the radial direction to the outside. As the refrigerant gas passes through the first diffuser flow path 63, the refrigerant gas is decelerated to a high pressure, and its kinetic energy is converted into internal energy. A plurality of vanes 65 are arranged in the middle of the first diffuser flow path 63 or in the vicinity of the outlet, and the refrigerant gas is rectified by the vanes 65.

The refrigerant gas with increased internal energy is guided to the inlet of the second impeller 52 through the gas flow path.
The second impeller 52 sucks the refrigerant from its inlet and increases the speed and pressure of the refrigerant in the same manner as the first impeller 51. This refrigerant is guided from the inside in the radial direction to the outside by the second diffuser channel 69 extending from the inside in the radial direction to the outside. As the refrigerant gas passes through the second diffuser flow path 69, the refrigerant gas is decelerated to a high pressure, and its kinetic energy is converted into internal energy. A plurality of vanes 71 are arranged in the middle of the second diffuser flow path 69 or in the vicinity of the outlet, and the refrigerant gas is rectified by the vanes 71. And this refrigerant gas is sent out from a discharge outlet.

  In the turbo compressor as described above, when the fluid suction flow rate by the impellers 51 and 52 is changed, for example, the fluid inflow angle to the second diffuser flow path 69 changes, so that the fluid blown out from the second impeller 52 This flow direction coincides with the arrangement direction of the plurality of vanes 71 arranged in the second diffuser flow path 69 at a certain suction flow rate, and a desirable diffuser effect is obtained. However, if the suction flow rate changes, the flow direction of the fluid blown out from the second impeller 52 and the arrangement direction of the vanes 71 do not coincide with each other, and a sufficient diffuser effect cannot be obtained.

Therefore, in patent document 1, it has taken the structure which can move one of a pair of parallel walls arrange | positioned at intervals in the axial direction which divides a diffuser flow path to an axial direction with respect to the other.
That is, a desired diffuser effect can be obtained by adjusting the position of one of the parallel walls so that the flow direction of the fluid blown out of the impeller and the vane arrangement direction coincide with the change in the fluid suction flow rate. I have to.

The pair of parallel walls face the axial direction and face each other, thereby defining a diffuser flow path. As shown in FIG. 11, the side surface 73a of the diffuser ring 73 forms one parallel wall, and the side surface 75a of the housing 75 forms the other parallel wall.
FIG. 12 shows a configuration for moving and adjusting the parallel walls described in Patent Document 1.
In Patent Document 1, the diffuser ring 73 is moved in the axial direction so that the pair of parallel walls are closely spaced.
The diffuser ring 73 is incorporated in the housing 75 so as to be rotatable in the circumferential direction and movable in the axial direction. That is, when the diffuser ring 73 is rotated in the circumferential direction, the diffuser ring 73 is incorporated in the housing 75 so as to move in the axial direction accordingly.

The configuration for this is as follows.
FIG. 12 shows a groove 77 formed on the outer peripheral surface of the diffuser ring 73, and FIG. 12 (A) is a partial side view of the second diffuser channel 69 viewed from the axial direction. ) Is an AA line arrow view of FIG. As can be seen from FIG. 12B, the groove 77 is formed to extend obliquely so that its axial position changes.
Such grooves 77 are formed at a plurality of locations on the outer peripheral surface of the second diffuser ring 73 at intervals in the circumferential direction.

  On the other hand, in the housing 75, when the diffuser ring 73 is assembled, protrusions 79 are formed in the plurality of grooves 77 of the diffuser ring 73 from the outside in the radial direction with a gap in the circumferential direction.

  FIG. 13 shows a variable mechanism for rotating the diffuser ring 73. The variable mechanism includes a bracket 81 attached to the diffuser ring 73, a shaft body 83 rotatably attached to the bracket, and a drive device 85 that linearly moves the shaft body 83.

With this configuration, when the driving device 85 linearly moves the shaft body 83, the diffuser ring 73 is rotated in the circumferential direction via the bracket 81 attached to the shaft body 83.
When the diffuser ring 73 rotates, the projection 79 formed in the circumferential direction on the housing 75 guides the movement of the diffuser ring 73 along the groove 77, but the groove 77 is formed to be inclined in the axial direction. The diffuser ring 73 not only rotates in the circumferential direction but also moves in the axial direction.
Thus, since the diffuser ring 73 moves in the axial direction, the pair of parallel walls can be brought close to and away from each other, and the flow direction of the fluid can be adjusted appropriately.
JP 2002-48098 A "Turbo compressor and refrigerator"

  However, in the parallel wall variable mechanism disclosed in Patent Document 1, when the diffuser ring 73 is rotated, the force concentrates on one place of the bracket 81 attached to the diffuser ring 73, so that an unreasonable stress acts on the bracket 81. Operation becomes unstable, such as twisting.

  Further, in Patent Document 1, a drive device is provided on the radially outer side of the diffuser ring, and the drive device rotates the diffuser ring by linearly moving the rod body from the radially outer side. The sealing performance deteriorates.

  Accordingly, a first object of the present invention is a turbo compressor capable of adjusting the width of a diffuser flow path, and an operation of moving a diffuser ring that divides the diffuser flow path in the axial direction for adjusting the width of the diffuser flow path. An object of the present invention is to provide a turbo compressor that can improve the stability of the compressor.

  A second object of the present invention is to provide a turbo compressor that can maintain high sealing performance even if a drive mechanism for driving a diffuser ring is provided.

  A third object of the present invention is a refrigerator equipped with a turbo compressor capable of adjusting the width of a diffuser flow path, for adjusting the width of the diffuser flow path, for adjusting the width of the diffuser flow path, An object of the present invention is to provide a refrigerator that can improve the stability of the operation of moving the diffuser ring that partitions the shaft in the axial direction.

  According to the present invention, in order to achieve the first object, the rotary shaft includes a rotary shaft that is rotationally driven, an impeller that is fixed to the rotary shaft and compresses gas, and a housing that accommodates the impeller inside thereof, and is provided in the radial direction. A turbo compressor incorporating a variable mechanism that changes the width of a diffuser flow path that extends from the inside to the outside and guides the gas accelerated by the impeller from the inside to the outside in the radial direction, the variable mechanism including the diffuser flow A diffuser ring that at least partially forms one of a pair of flow path walls sandwiching the path in the axial direction; a support structure that is fixed to the housing and supports the diffuser ring so as to be movable in the axial direction; and the support structure A plurality of oscillating members provided on the body at intervals in the circumferential direction and capable of oscillating with respect to the support structure, and each oscillating member and diffuser ring , And a swinging force applied to a plurality of swinging members, and a connecting member that converts the swinging motion of the swinging member into an axial linear motion so that the diffuser ring moves in the axial direction when each swinging member swings. A turbocompressor comprising: a drive mechanism for supplying a swinging force; and a transmission means for transmitting a swinging force from the drive mechanism to the swinging member so that the plurality of swinging members swings synchronously. Is provided.

In the above configuration, a plurality of oscillating members for moving the diffuser ring in the axial direction are arranged in the circumferential direction, and the transmission means is arranged so that the plurality of oscillating members are oscillated synchronously from the drive mechanism. Since the oscillating force is transmitted to the oscillating member, the oscillating force from the drive mechanism is prevented from acting on one place and is appropriately distributed to the oscillating members arranged at a plurality of places.
Then, the distributed swinging force is converted from the swinging motion of the swinging member to the linear motion by the corresponding connecting member and applied to the diffuser ring.
As described above, since the swinging force from the drive mechanism is appropriately distributed and applied to the diffuser ring, the operation of moving and adjusting the diffuser ring in the axial direction can be stably performed for adjusting the diffuser channel width. .

  According to a preferred embodiment of the present invention, the transmission means is a linear member extending in the circumferential direction and having a plurality of swing members fixed thereto.

  Thus, since the transmission means is a linear member extending in the circumferential direction and having a plurality of swinging members fixed thereto, the transmission means can be simply configured as a linear member.

  According to a preferred embodiment of the present invention, support members that support the linear members and stretch in the circumferential direction are fixed to the support structure at intervals in the circumferential direction, and each support member is a linear member. Is inserted to support the linear member and has a concave portion facing outward in the radial direction, and the concave portion has a width in the axial direction that allows the linear member to move in the axial direction.

  Thus, the linear member support means for supporting the linear member and stretching it in the circumferential direction has a concave portion in which the linear member is inserted and supports the linear member, and the concave portion allows axial movement of the linear member. Therefore, the supporting member can stretch the linear member in the circumferential direction while allowing the linear member to move in the axial direction.

  Preferably, one end portion in the axial direction of each connecting member is movably coupled to the swinging member so that it moves only in the axial direction when the swinging member swings, and the other end portion in the axial direction of each connecting member is It is fixed to the diffuser ring.

  Thus, each connecting member can move with respect to the swinging member, but is fixed to the diffuser ring, so that when each connecting member converts the swinging of the swinging member into a linear motion in the axial direction, The connecting member can move and adjust the position of the diffuser ring only in the axial direction.

  Preferably, each oscillating member is attached with an attachment member that is rotatable with respect to the oscillating member about a rotation axis parallel to the oscillating axis, and the linear member is fixed to each attachment member. ing.

  As described above, the linear member is attached to the swinging member via the mounting member that is rotatable with respect to the swinging member about the rotation axis parallel to the swinging shaft. Even in this case, the linear member can be kept in the same posture.

  According to a preferred embodiment of the present invention, in order to achieve the second object, the drive mechanism is coupled to the swing member coaxially with any swing shaft of the plurality of swing members and is driven to rotate. Drive shaft.

Thus, the drive mechanism is a drive shaft that is coupled to the swing member coaxially with the swing shaft of any of the plurality of swing members and is rotationally driven. Even if the motor is arranged radially outward of the diffuser ring, the output shaft directed radially inward is rotated to transmit the swinging force. Therefore, compared with the case where the power transmission member is linearly moved from the outside in the radial direction to the inside, the sealing performance in the radial direction of the turbo compressor can be maintained high.
Further, since the swing member is swung by the rotation of the drive shaft, the position of the diffuser ring can be adjusted by adjusting the rotation angle of the drive shaft.

  According to the present invention, in order to achieve the third object, a turbo compressor that boosts the gas refrigerant, a condenser that condenses and liquefies the refrigerant boosted by the turbo compressor, and an expansion that depressurizes the refrigerant liquefied by the condenser. A refrigerator that evaporates and evaporates the refrigerant depressurized by the expansion valve, wherein the refrigerant heat-exchanged with the cooling medium in the evaporator is sucked into the turbo compressor, The turbo compressor includes a rotary shaft that is rotationally driven, an impeller that is fixed to the rotary shaft and compresses gas, and a housing that accommodates the impeller on the inside thereof. And a variable mechanism for changing the width of the diffuser flow path for guiding the gas accelerated by the impeller from the inside to the outside in the radial direction is incorporated. A diffuser ring that at least partially forms one of a pair of channel walls sandwiched, a support structure that is fixed to the housing and supports the diffuser ring so that it can move in the axial direction, and a circumferential direction on the support structure A plurality of oscillating members provided at intervals and oscillating with respect to the support structure, each oscillating member and the diffuser ring are connected, and when each oscillating member oscillates, the diffuser ring is moved in the axial direction. A connecting member that converts the swinging motion of the swinging member into an axial linear motion so as to move, a drive mechanism that applies a swinging force to the plurality of swinging members, and the plurality of swinging members are swung synchronously. Thus, there is provided a refrigerator comprising transmission means for transmitting a swinging force from a drive mechanism to a swinging member.

In the turbo compressor of the refrigerator having the above-described configuration, a plurality of swing members for moving the diffuser ring in the axial direction are arranged in the circumferential direction, and the transmission means is swung in synchronization with the plurality of swing members. As described above, the oscillating force from the drive mechanism is transmitted to the oscillating member, so that the oscillating force from the drive mechanism is prevented from concentrating on one place, and the oscillating members disposed at a plurality of locations are Appropriately distributed.
Therefore, since the swinging force from the drive mechanism is appropriately distributed and applied to the diffuser ring via the swinging member and the connecting member, the movement of the diffuser ring in the axial direction can be adjusted stably.

  In the present invention described above, the stability of the operation of moving the diffuser ring that divides the diffuser flow path in the axial direction can be increased in order to adjust the diffuser flow path width.

  A preferred embodiment of the present invention will be described with reference to the drawings. In addition, the same code | symbol is attached | subjected to the common part in each figure, and the overlapping description is abbreviate | omitted.

FIG. 1 is a configuration diagram of a refrigerator 10 according to an embodiment of the present invention. As shown in FIG. 1, the refrigerator 10 is a two-stage turbo chiller, and has a turbo compressor 20 having two-stage impellers 2 and 3 that boost refrigerant gas in two stages, and the turbo compressor 20 boosts the refrigerant gas. A condenser 7 for condensing and liquefying the refrigerant, an intermediate cooler 11 having two expansion valves 8 and 9 for depressurizing the refrigerant liquefied in the condenser 7 in two stages, and evaporating and evaporating the refrigerant depressurized by the expansion valve 9 And an evaporator 12.
The gas phase component in the intermediate cooler is supplied to the second stage impeller 3 of the turbo compressor 20 through the bypass pipe 13.

  In the refrigerator 10 having such a configuration, a cooling medium (for example, cooling water) is passed through the evaporator 12, and the cooling medium is cooled by exchanging heat with the refrigerant and used for cooling and freezing. The On the other hand, the refrigerant having exchanged heat with the cooling medium in the evaporator 12 is again sucked into the turbo compressor 20.

  In FIG. 1, an output shaft 15 of the drive motor 14 and a rotary shaft 17 of the turbo compressor 20 are engaged with each other by a small gear 15 a and a large gear 17 a that transmit the rotational force of the drive motor 14 to the rotary shaft 17. It is fixed. The number of teeth of the small gear 15a and the large gear 17a can be set so that the rotation speed of the rotary shaft 17 is optimized.

FIG. 2 is a partially enlarged cross-sectional view showing the configuration of the turbo compressor 20 provided in the refrigerator 10 described above. The turbo compressor 20 has a rotating shaft on which a driving motor 14 (shown only in FIG. 1) as a driving source and a large gear 17a that engages with a small gear 15a fixed on an output shaft 15 of the driving motor 14 are fixed. 17, a first-stage impeller 2 and a second-stage impeller 3 that are fixed to the rotary shaft 17 at an axial interval, and a housing 19 that surrounds the first-stage impeller 2 and the second-stage impeller 3. .
An inlet nozzle member 23 having a suction port 21 for introducing a refrigerant gas into the first stage impeller 2 is attached to the refrigerant gas suction side of the housing 19. The inlet nozzle member 23 has a suction capacity. An inlet guide vane 25 for control is provided.

The refrigerant gas sucked from the suction port 21 by the rotation of the first stage impeller 2 is accelerated by the action of the first stage impeller 2.
The refrigerant gas accelerated by the first stage impeller 2 is sent to the first diffuser channel 26 communicating with the outlet of the first stage impeller 2. The first diffuser channel 26 extends from the radially inner side to the outer side and guides the refrigerant gas accelerated by the first stage impeller 2 from the radially inner side to the outer side.

The refrigerant gas is decelerated to a high pressure in the process of passing through the first diffuser flow path 26.
A plurality of vanes 27 are arranged in the circumferential direction in the middle of the first diffuser flow path 26 or in the vicinity of the outlet. These vanes 27 have a function of rectifying the refrigerant gas passing through the first diffuser flow path 26.

  The refrigerant gas that has passed through the first diffuser flow path 26 is changed in the flow direction radially inward by a return bend 28 that is a flow path communicating with the first diffuser flow path 26 on the radially outer side, Guided to the second stage impeller 3.

  The refrigerant gas guided to the second stage impeller 3 is accelerated again by the rotation of the second stage impeller 3 and sent to the second diffuser flow path 31 communicating with the outlet of the second stage impeller 3.

  Similar to the first diffuser flow path 26, the second diffuser flow path 31 extends from the inside in the radial direction to the outside and guides the refrigerant gas accelerated by the second stage impeller 3 from the inside in the radial direction to the outside.

The refrigerant gas is decelerated to a high pressure in the process of passing through the second diffuser flow path 31.
A plurality of vanes 29 are arranged in the circumferential direction in the middle of the second diffuser flow path 31 or in the vicinity of the outlet. These vanes 29 have a function of rectifying the refrigerant gas passing through the second diffuser flow path 31.
The refrigerant gas that has passed through the second diffuser flow path 31 is discharged to the outside of the turbo compressor 20 via the scroll chamber 32.

  Thus, the refrigerant gas sucked into the turbo compressor 20 passes through the first stage impeller 2, the first diffuser flow path 26, the second stage impeller 3, and the second diffuser flow path 31, and thereby has two stages. Is pressurized and discharged from the turbo compressor 20.

In the turbo compressor 20 as described above, for example, in order to change the boosting capacity, it is sufficient to change the suction flow rate of the refrigerant gas by changing the rotation speed of the drive motor 14, that is, the rotation speed of the rotary shaft 17. Diffuser effect may not be obtained.
That is, when the suction flow rate changes, the flow direction of the fluid blown out from the first stage impeller 2 or the second stage impeller 3 and the vane 27 provided in the middle of the first diffuser flow path 26 or the second diffuser flow path 31 or in the vicinity of the outlet. Alternatively, the arrangement direction of 29 does not match, and a sufficient diffuser effect cannot be obtained.

Therefore, in the present embodiment, the diffuser is arranged so that the flow direction of the fluid blown from the first stage impeller 2 or the second stage impeller 3 and the arrangement direction of the vanes 27 or 29 coincide with the suction flow rate of the refrigerant gas. A variable mechanism for adjusting the width of the flow path is incorporated in the turbo compressor 20.
In the following, a variable mechanism for adjusting the width of the second diffuser flow path 31 will be described. However, the width of the first diffuser flow path 26 can also be adjusted by a similar variable mechanism.

  The second diffuser flow path 31 is partitioned by a pair of flow path walls that sandwich the second diffuser flow path 31 in the axial direction. In the example of FIG. 2, as shown in FIG. 2, the side surface of the diffuser ring 33 forms one of a pair of flow path walls, and the side surface formed on the housing 19 forms the other of the pair of flow path walls. ing.

3, 4, and 5 show the variable mechanism 30 that adjusts the axial position of the diffuser ring 33 in order to adjust the width of the second diffuser flow path 31. 3 is an enlarged view of a portion X indicated by a broken line in FIG. 2, FIG. 4 is a view taken along line AA in FIG. 2, and FIG. 5 is a view taken along line AA in FIG. In addition, in FIG. 3 to FIG.
This variable mechanism 30 includes a diffuser ring 33, an annular seal ring 35 that is a support structure that supports the diffuser ring 33 so as to be movable in the axial direction, and a swinging member mounting portion 35a of the seal ring 35 in the circumferential direction. A plurality of oscillating members 37 that are provided at intervals and can be oscillated with respect to the seal ring 35 around an oscillating shaft 36 perpendicular to the axial direction, and each oscillating member 37 and the diffuser ring 33 are connected. When each swing member 37 swings, a connecting member 39 that converts the swing motion of the swing member 37 into an axial linear motion so that the diffuser ring 33 moves in the axial direction, and swing force to the swing member 37. The linear member 43 which is a transmission means for transmitting the swinging force from the drive shaft 34 to the swinging member 37 so as to swing the drive shaft 34 and the plurality of swinging members 37 synchronously. , And a. The seal ring 35 as a support structure is fixed to the housing 19.

  As shown in FIGS. 3 to 5, the diffuser ring 33 is formed with an annular protrusion 33 a on the radially inner side, and the amount of protrusion of the annular protrusion 33 a to the second diffuser flow path 31 causes the second diffuser flow path 31. The width is adjusted.

In the example of FIG. 3, the drive shaft 34 for oscillating the oscillating member 37 oscillates coaxially with the oscillating shaft 36 of any one of the oscillating members 37. The shaft is coupled and fixed to the member 37. A knob 38 is attached to the other end of the drive shaft 34, and the swinging member 37 is swung with respect to the seal ring 35 by manually rotating the drive shaft 34 from the outside of the turbo compressor 20. Can be made.
The drive shaft 34 may be an output shaft of a rotary motor such as a servo motor. In this case, the rotary motor is fixed to the housing 19 on the radially outer side of the diffuser ring 33, and its output shaft is coupled and fixed to the swing member 37 coaxially with the swing shaft 36 of the swing member 37. It extends so that. Therefore, when the output shaft of the rotary motor rotates, the swing member 37 is driven to swing around the swing shaft 36.
The drive shaft 34 and the knob 38 or the rotary motor constitute a drive mechanism, but the drive mechanism may be constituted by other appropriate ones.

6 shows the swinging member 37, FIG. 6 (A) is a view taken along line BB in FIG. 4, and FIG. 6 (B) is a view taken along line CC in FIG. is there. In FIG. 6, a mounting member described later is omitted, and in FIG. 6A, the connecting member 39 is indicated by a two-dot chain line.
As shown in FIG. 6, the swing member 37 includes a horizontally long engagement hole 37 a into which an engagement pin 39 a fixed to a connecting member 39 described later is inserted and engaged, and a swing member of a seal ring 35 described later. A swing hole 37b in which a swing pin 35b fixed to the mounting portion 35a is rotatably inserted, and a rotary pin fixed to a mounting member to be described later for mounting the linear member 43 are loosely inserted in a rotatable manner. Rotation holes 37c are formed.
The swing pin 35b is loosely fitted from one side of the swing member 37 to the middle of the swing hole 37b, and the drive shaft 34 is inserted from the other side of the swing member to the middle of the swing hole 37b to swing. It can be configured to be fixed to the inner peripheral surface of the hole 37b. Thus, when the drive shaft rotates, the swing member 37 swings with respect to the seal ring 35, but when the drive shaft rotates with another configuration, the swing member 37 swings with respect to the seal ring 35. You may make it do.

  As shown in FIG. 4, a plurality of (three in the example of FIG. 4) swing pins 35b for mounting the swing member 37 are spaced apart in the circumferential direction on the swing member mounting portion 35a of the seal ring 35. Is fixed.

In the example of FIG. 4, the connecting member 39 is a cylindrical member extending in the axial direction, but is not limited to the cylindrical shape, and may have another shape extending in the axial direction.
As shown in FIG. 6B, an engagement pin 39 a to be inserted into the engagement hole 37 a of the swing member 37 is fixed to one end portion of the connecting member 39. That is, the engaging pin 39 a engages with the engaging hole 37 a of the swinging member 37, so that one end of the connecting member 39 is coupled to the swinging member 37 and the other end of the connecting member 39 is connected to the diffuser ring 33. Thus, the swinging member 37 and the diffuser ring 33 are coupled to each other.
In the example of FIG. 4, the other end of the connecting member 39 is fixed to the inner peripheral surface of the diffuser ring 33, but may be fixed to another appropriate location of the diffuser ring 39.

FIG. 7 is a view showing the swinging operation of the swinging member 37 to which the connecting member 39 is coupled as described above. When the swing member 37 swings about the swing shaft 36 from the position of FIG. 7A, the position of FIG. 7B is obtained. While swinging, the engaging pin 39 a of the connecting member 39 moves along the engaging hole 37 a of the swinging member 37. That is, when the swinging member 37 swings, the connecting member 39 moves along the engaging hole 37a with respect to the swinging member 37, so that the connecting member 39 can be smoothly pivoted without applying an excessive force. Can only move in the direction.
Therefore, when the swinging member 37 is swung, the connecting member 39 smoothly moves linearly in the axial direction. Therefore, the position of the diffuser ring 33 fixed to the connecting member 39 can be moved and adjusted smoothly in the axial direction. it can.

On the other hand, as shown in FIG. 4, the linear member 43 is stretched in the circumferential direction, and a plurality of swinging members 37 are fixed to the linear member 43 at intervals. The linear member 43 is, for example, a wire, but other appropriate members may be used as the linear member 43.
In order to extend and stretch the linear member 43 in the circumferential direction, a plurality of support members 47 are fixed at intervals in the circumferential direction.
FIG. 8 is a view taken along the line D-D in FIG. 4 and shows the support member 47. As shown in FIG. 8, the support member 47 has a recess 47 a into which the linear member 43 is inserted and supports the linear member 43. The recess 47a has a width in the axial direction that allows the linear member 43 to move in the axial direction. Thereby, the linear member 43 can be stretched in the circumferential direction while allowing the linear member 43 to move in the axial direction.

The inner surface of the recess 47a of each support member 47 is a curved surface in the circumferential direction so that the linear member 43 can move in the circumferential direction. For example, as shown in FIG. It is good also as a shape which combined the flange 47b whose outer diameter is larger than this cylinder on the upper and lower surfaces of the cylinder corresponding to.

The support member 47 includes an axially fixed pin fixed to the seal ring 35 and a roller attached to the pin and rotatable about the pin, and the linear member 43 is inserted into the roller as described above. It is also possible to form a recessed portion 47a.
With this configuration, when the swing member 37 swings, the linear member 43 can move more smoothly in the circumferential direction.

9 shows a structure for attaching the linear member 43 to the swinging member 37. FIG. 9 (A) is a view taken along the line EE of FIG. 4, and FIG. 9 (B) is a diagram of FIG. It is a CC line arrow directional view. In addition, the connection member 39 mentioned above in FIG.9 (B) is drawn with the dashed-two dotted line.
As shown in FIG. 9B, a rotation pin 45 a is rotatably fitted in the rotation hole 37 c of the swing member 37. The rotation pin 45a is fixed to the attachment member 45, and the attachment member 45 is further formed with a through hole through which the linear member 43 passes.
The linear member 43 may be loosely passed through the through hole so as to be movable along the through hole, or the linear member 43 may be passed through the through hole and fixed to the attachment member 45 by an appropriate fixing means. .

The effects of the variable mechanism 30 having the above-described configuration will be described.
When the drive shaft 34 is rotated by the knob 38 or the rotary motor, the drive shaft 34 is coupled to the swing shaft 36, so that the swing member 37 is driven to swing around the swing shaft 36.
Even if the knob 34 and the rotary motor are arranged on the radially outer side of the diffuser ring 33, the drive shaft 34 that is directed radially inward is rotated to transmit the swinging force, so that the power transmission member is linearly moved from the radially outer side to the inner side. As compared with the case where the turbo compressor 20 is moved, the sealing performance in the radial direction of the turbo compressor 20 can be maintained high.
Further, since the rotation of the drive shaft 34 is a swinging force, the axial position of the diffuser ring 33 can be adjusted by adjusting the rotation angle of the drive shaft 34.

  Further, as described above, the linear member 43 is stretched so as to extend in the circumferential direction, and a plurality of swinging members 37 are fixed to the linear member 43. When it is to be swung, this rocking force is transmitted to the other rocking member 37 by the linear member 43. Accordingly, the plurality of swing members 37 can be swung in synchronization.

  As described above, when the plurality of swinging members 37 swings synchronously, the linear members 43 fixed to the swinging members 37 also move simultaneously. Since the recess 47a of the support member 47 supports the linear member 43 so as to be movable in the circumferential direction as described above, the swing member 37 swings. Even so, the linear member 43 can move freely while being supported by the support member 47. Therefore, even if the plurality of swinging members 37 swings synchronously, it is possible to prevent an unreasonable force from acting on the linear member 43.

Thus, when the plurality of swing members 37 are driven to swing around the swing shaft 36 perpendicular to the axial direction, the position from FIG. 7A to the position in FIG. 7B. The swing position of the swing member 37 changes.
At this time, the engaging pin 39 a fixed to one end of the connecting member 39 moves along the engaging hole 37 a of the swinging member 37, but the other end of the connecting member 39 is fixed to the diffuser ring 33. Therefore, the connecting member 39 can move only in the axial direction.

Further, when each swinging member 37 swings from the position of FIG. 10A to the position of FIG. 10B, the rotation pin 45a fitted in the rotation hole 37c of the swinging member 37 is rotatable. Therefore, the attachment member 45 can always stay in a plane perpendicular to the axial direction. That is, since the linear member 43 is fixed to the swinging member 37 via the mounting member 45 that can maintain a constant posture, the linear member 43 is kept in a constant posture even if the swinging member 37 swings. Can be kept in.
Therefore, an excessive stress is prevented from acting on the linear member 43 when the swinging member 37 swings.

  As described above, according to the embodiment of the present invention, the plurality of swinging members 37 for moving the diffuser ring 33 in the axial direction are arranged in the circumferential direction, and the plurality of swinging members 37 are swung in synchronization. As described above, the linear member 43 transmits the swinging force from the drive shaft 34 to the swinging member 37, so that the swinging force from the drive shaft 34 is prevented from acting on one place and is applied to a plurality of places. It is appropriately distributed to the rocking member 37 arranged. The distributed swinging force is converted from a swinging motion of the swinging member 37 into a linear motion by the corresponding connecting member 39 and applied to the diffuser ring 33. Thus, since the swinging force of the drive mechanism is appropriately distributed and applied to the diffuser ring 33, the operation of moving and adjusting the diffuser ring 33 in the axial direction can be stably performed in order to adjust the diffuser flow path width. it can.

  In addition, this invention is not limited to embodiment mentioned above, Of course, a various change can be added in the range which does not deviate from the summary of this invention.

It is a block diagram of the refrigerator by embodiment of this invention. It is a fragmentary sectional view of the turbo compressor with which the refrigerator of FIG. 1 was equipped. It is an enlarged view of the part X shown with the broken line of FIG. 2, and has shown the structure of the variable mechanism which moves the diffuser ring by embodiment of this invention. FIG. 3 is a view taken along line AA in FIG. 2, showing a configuration of a variable mechanism that moves the diffuser ring according to the embodiment of the present invention. It is an AA arrow directional view of FIG. FIG. 6A is a view taken along line B-B in FIG. 4, and FIG. 6B is a view taken along line C-C in FIG. 4. It is a figure which shows rocking | fluctuation operation | movement of a rocking | swiveling member. It is the DD sectional view taken on the line of FIG. 4, and has shown the structure of the supporting member. FIG. 9A is a view taken along the line E-E in FIG. 4, and FIG. 9B is a view taken along the line C-C in FIG. 4. The position of the attachment member when the swing member swings is shown. The structure of the turbo compressor of patent document 1 is shown. It is a block diagram of the diffuser ring of patent document 1. It is a block diagram of the variable mechanism which moves the diffuser ring of patent document 1. FIG.

Explanation of symbols

2 First stage impeller 3 Second stage impeller 7 Condensers 8 and 9 Expansion valve 10 Refrigerator 11 Intermediate cooling 12 Evaporator 13 Bypass pipe 14 Drive motor 15 Output shaft 15a Small gear 17 Rotating shaft 17a Large gear 19 Housing 20 Turbo compression Machine 21 Suction port 23 Inlet nozzle member 25 Inlet guide vane 26 First diffuser flow path 27 Vane
30 Variable mechanism 31 Second diffuser flow path 33 Diffuser ring 34 Drive shaft (drive mechanism)
35 Seal ring (support structure)
36 oscillating shaft 37 oscillating member 37a engaging hole 37b oscillating hole 37c rotating hole 39 connecting member 39a engaging pin 43 linear member (transmission means)
45 Mounting member 45a Rotating pin 47 Support member 47a Cylinder 47b 鍔

Claims (7)

A rotary shaft that is rotationally driven, an impeller that is fixed to the rotary shaft and compresses gas, and a housing that accommodates the impeller inside, and that extends from the inside in the radial direction to the outside and that accelerates the gas accelerated by the impeller in the radial direction A turbo compressor incorporating a variable mechanism for changing the width of the diffuser flow path leading from the inside to the outside,
The variable mechanism is
A diffuser ring that at least partially forms one of a pair of flow path walls sandwiching the diffuser flow path in the axial direction;
A support structure fixed to the housing and supporting the diffuser ring so as to be movable in the axial direction;
A plurality of swing members provided on the support structure at intervals in the circumferential direction and swingable with respect to the support structure;
A connecting member that connects each oscillating member and the diffuser ring, and converts the oscillating motion of the oscillating member into an axial linear motion so as to move the diffuser ring in the axial direction when each oscillating member oscillates;
A drive mechanism for applying a swinging force to a plurality of swinging members;
A turbo compressor comprising: transmission means for transmitting a swinging force from the drive mechanism to the swinging member so that the plurality of swinging members swings synchronously.   The turbo compressor according to claim 1, wherein the transmission means is a linear member extending in a circumferential direction and having a plurality of swing members fixed thereto. A support member that supports the linear member and stretches in the circumferential direction is fixed to the support structure at intervals in the circumferential direction.
Each support member has a concave portion that is fitted with a linear member and supports the linear member and faces radially outward, and the concave portion has a width in the axial direction that allows the linear member to move in the axial direction. The turbo compressor according to claim 2.   One end of each connecting member in the axial direction is movably coupled to the swinging member so that it moves only in the axial direction when the swinging member swings, and the other end in the axial direction of each connecting member is connected to the diffuser ring. The turbo compressor according to claim 1, wherein the turbo compressor is fixed.   Each oscillating member is attached with an attachment member that is rotatable relative to the oscillating member about a rotation axis parallel to the oscillating axis, and the linear member is fixed to each attachment member. The turbo compressor according to claim 2.   2. The turbo compression according to claim 1, wherein the drive mechanism is a drive shaft that is coupled to the swing member coaxially with a swing shaft of a plurality of swing members and is driven to rotate. Machine. A turbo compressor that boosts the gas refrigerant, a condenser that condenses and liquefies the refrigerant boosted by the turbo compressor, an expansion valve that decompresses the refrigerant liquefied by the condenser, and an evaporator that evaporates and evaporates the refrigerant decompressed by the expansion valve And a refrigerant in which the refrigerant heat-exchanged with the cooling medium in the evaporator is sucked into the turbo compressor,
The turbo compressor includes a rotary shaft that is driven to rotate, an impeller that is fixed to the rotary shaft and compresses gas, and a housing that houses the impeller inside.
The turbo compressor incorporates a variable mechanism that changes the width of the diffuser flow path that extends from the inside in the radial direction to the outside and guides the gas accelerated by the impeller from the inside in the radial direction to the outside,
The variable mechanism is
A diffuser ring that at least partially forms one of a pair of flow path walls sandwiching the diffuser flow path in the axial direction;
A support structure fixed to the housing and supporting the diffuser ring so as to be movable in the axial direction;
A plurality of swing members provided on the support structure at intervals in the circumferential direction and swingable with respect to the support structure;
A connecting member that connects each oscillating member and the diffuser ring, and converts the oscillating motion of the oscillating member into an axial linear motion so as to move the diffuser ring in the axial direction when each oscillating member oscillates;
A drive mechanism for applying a swinging force to a plurality of swinging members;
A refrigerator comprising: a transmission unit configured to transmit a swinging force from the drive mechanism to the swinging member so that the plurality of swinging members swings synchronously.

Images