JP2005016454A - Pulsation reduction structure in equipment with gas passage - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide pulsation reduction structure for exerting sufficient pulsation reduction effect and suppressing pressure loss, in equipment with gas passage such as a compressor. <P>SOLUTION: An outlet hole 311 is formed in an peripheral wall of a front housing 31, and a pipe 35 is fit and fixed into the outlet hole 311. A throttle passage 381 and a pressure recovery passage 391 are formed in the pipe 35. A discharge port 231 and a discharge chamber 32 are a part of the gas passage in the compressor, and the discharge chamber 32 is a muffler constituting a part of the gas passage. The pressure recovery passage 391 is formed on the downstream side of the throttle passage 381 to constitute a combination passage 40 formed on the downstream side of the discharge chamber 32. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a pulsation reducing structure in a device having a gas flow path.
[0002]
[Prior art]
In the scroll compressor disclosed in Patent Document 1, an oil separator is provided in a front housing. The oil separation chamber constituting the oil separator communicates with a discharge chamber formed on the back surface of the fixed scroll, and a cylinder member constituting the oil separator is accommodated in the oil separation chamber. The refrigerant gas in the discharge chamber is introduced into the oil separation chamber, and the lubricating oil contained in the refrigerant gas introduced into the oil separation chamber is separated from the refrigerant gas.
[0003]
The cylinder member constituting the oil separator also has a function of reducing discharge pulsation.
[0004]
[Patent Document 1]
JP 2002-285981 A
[0005]
[Problems to be solved by the invention]
In order to obtain a sufficient pulsation reducing effect, it is necessary to reduce the inner diameter of the cylindrical member. However, if the inner diameter of the cylindrical member is made too small, a large pressure loss occurs. Therefore, it has been difficult to reduce the inner diameter of the cylindrical member so that a sufficient pulsation reducing effect can be obtained.
[0006]
An object of the present invention is to provide a pulsation reduction structure that can provide a sufficient pulsation reduction effect and can suppress pressure loss in an apparatus having a gas flow path such as a compressor.
[0007]
[Means for Solving the Problems]
The present invention is directed to an apparatus that includes a muffler for reducing pulsation from a pulsation source as a part of a gas flow path. In the invention of claim 1, the upstream side or the downstream side of the muffler with respect to the gas flow path. A combined flow path in which the throttle flow path and the pressure recovery flow path are combined in series, the pressure recovery flow path is provided downstream of the throttle flow path with respect to the gas flow path, and the gas flow path is The muffler was disposed between the pulsation source and the synthesis channel.
[0008]
Since the pressure recovery channel recovers the pressure of the gas that has passed through the throttle channel, the passage cross-sectional area in the throttle channel can be reduced, and the pulsation reduction effect can be enhanced.
According to a second aspect of the present invention, in the first aspect, the synthetic flow path is provided in a pipe cylinder, and the pipe is disposed in the gas flow path so that the gas in the gas flow path flows through the synthetic flow path. Arranged.
[0009]
The inside of the pipe is suitable as a place for forming the synthesis channel.
According to a third aspect of the present invention, in the first aspect, the plurality of synthetic flow paths are provided in parallel.
[0010]
The length of the pressure recovery channel needs to be increased as the difference in diameter between the throttle channel and the gas channel increases. If a plurality of synthesis channels are provided in parallel, the length of the pressure recovery channel can be shortened.
[0011]
According to a fourth aspect of the present invention, in any one of the second and third aspects, a tapered passage is connected in series to the throttle channel, and the small diameter portion side of the tapered shape is connected to the throttle channel. Connected.
[0012]
Such a connection configuration is effective in reducing the channel resistance against the gas flow.
In the invention of claim 5, the device is a compressor.
The compressor is suitable as an application target of the present invention.
[0013]
DETAILED DESCRIPTION OF THE INVENTION
A first embodiment in which the present invention is embodied in a scroll compressor will be described below with reference to FIGS. 1 (a) and 1 (b).
[0014]
As shown in FIG. 1A, a shaft support member 13 and a fixed scroll 11 are fitted and fixed to the rear housing 12, and a front housing 31 is joined to the rear housing 12 and the fixed scroll 11. The rear housing 12 and the front housing 31 constitute an entire housing of the scroll compressor 10 as a device. A rotating shaft 14 is rotatably supported on the end wall of the rear housing 12 and the shaft support member 13 via radial bearings 15 and 16.
[0015]
An eccentric shaft 17 is integrally formed at the end of the rotating shaft 14 that passes through the shaft support member 13 and protrudes toward the fixed scroll 11. The center axis of the eccentric shaft 17 is set at a position that is eccentric from the rotation center axis of the rotating shaft 14. A bush 18 is fitted and supported on the eccentric shaft 17, and a balance weight 19 is integrally formed on the bush 18. A movable scroll 20 is supported on the bush 18 via a radial bearing 21 so as to be rotatable relative to the fixed scroll 11. The radial bearing 21 is accommodated in a cylinder of a cylinder portion 221 that protrudes from the back surface of the movable scroll substrate 22 of the movable scroll 20.
[0016]
The fixed scroll substrate 23 and the fixed spiral wall 24 of the fixed scroll 11 and the movable scroll substrate 22 and the movable spiral wall 25 of the movable scroll 20 form sealed spaces So and S1. The movable scroll 20 revolves with the rotation of the eccentric shaft 17, and the balance weight 19 cancels the centrifugal force associated with the revolving motion of the movable scroll 20.
[0017]
As shown in FIG. 1A, a plurality of (three or more) rotation prevention pins 27 having a cylindrical shape are fixed to the movable scroll substrate 22. The shaft support member 13 has circular rotation prevention holes 131 of the same number as the rotation prevention pins 27 arranged in the circumferential direction. The end of the rotation prevention pin 27 is inserted into the rotation prevention hole 131.
[0018]
A stator 29 is fixed to the inner peripheral surface of the rear housing 12, and a rotor 30 is fixed to the rotating shaft 14. When the stator coil 291 of the stator 29 is energized, the rotor 30 and the rotary shaft 14 rotate integrally. The stator 29 and the rotor 30 constitute an electric motor.
[0019]
The movable scroll 20 revolves with the rotation of the eccentric shaft 17 that rotates integrally with the rotary shaft 14. Along with the revolution of the movable scroll 20, refrigerant gas of an external refrigerant circuit (not shown) is introduced into the suction chamber 112 in the peripheral wall 111 from the inlet 26 formed in the peripheral wall of the rear housing 12 and the peripheral wall 111 of the fixed scroll 11. The refrigerant gas introduced into the suction chamber 112 flows between the fixed scroll substrate 23 and the movable scroll substrate 22 from the peripheral sides of the scrolls 11 and 20. Lubricating oil is enclosed in the refrigeration circuit including the compressor, and the lubricating oil flows together with the refrigerant gas.
[0020]
As the movable scroll 20 revolves, the peripheral surface of the rotation prevention pin 27 comes into sliding contact with the peripheral surface of the rotation prevention hole 131, and the movable scroll 20 revolves without rotating. The sealed spaces S <b> 1 and So converge toward the center of both scrolls 11 and 20 while the volume decreases with the revolution of the movable scroll 20.
[0021]
As shown in FIG. 1A, a discharge chamber 32 is formed in the front housing 31. The refrigerant gas compressed by reducing the volume of the sealed spaces S1 and So is discharged into the discharge chamber 32 by pushing the discharge valve 33 away from the discharge port 231 formed in the fixed scroll substrate 23. The opening degree of the discharge valve 33 is regulated by the retainer 34. The compression reaction force in the sealed spaces S <b> 1 and So against the movable scroll 20 is received by the shaft support member 13.
[0022]
An outlet hole 311 is formed in the peripheral wall of the front housing 31, and a pipe 35 is fitted and fixed to the outlet hole 311. As shown in FIG. 1B, the pipe 35 includes a fitting part 351, a throttle part 38, and a diffuser part 39. The throttle portion 38, the diffuser portion 39, and the fitting portion 351 are arranged in series in this order in the flow direction of the refrigerant gas from the discharge chamber 32 to the outside of the compressor via the outlet hole 311. That is, the throttle channel 381 in the cylinder of the throttle unit 38 and the pressure recovery channel 391 in the cylinder of the diffuser unit 39 are connected in series in this order from the discharge chamber 32 toward the outside of the compressor. .
[0023]
The pipe 35 is fitted into the outlet hole 311 via the fitting portion 351. The inner diameter of the fitting part 351 is larger than the inner diameter of the diffuser part 39 and the inner diameter of the throttle part 38. The inner diameter of the throttle portion 38 is constant, and the inner diameter of the diffuser portion 39 is gradually increased from the throttle portion 38 side toward the fitting portion 351 side. The expansion angle θ1 (shown in FIG. 1B) of the pressure recovery flow path 391 of the diffuser portion 39 is set to 20 ° or less.
[0024]
When the discharge valve 33 is pushed away from the discharge port 231 and the refrigerant gas is discharged into the discharge chamber 32, the refrigerant gas collides with the inner wall surface of the front housing 31 or the flow direction of the refrigerant gas changes into the cylinder of the pipe 35. Therefore, the lubricating oil contained in the refrigerant gas is separated from the refrigerant gas. The lubricating oil separated from the refrigerant gas is stored at the bottom of the discharge chamber 32. The bottom of the discharge chamber 32 communicates with the back pressure chamber 37 on the back side of the movable scroll substrate 22 via the return passage 36, and the lubricating oil accumulated in the bottom of the discharge chamber 32 is returned to the return passage 36 and the back pressure chamber. 37 is used for lubrication of the radial bearing 15 and the radial bearing 21. The refrigerant gas in the discharge chamber 32 passes through the inside of the pipe 35 to the external refrigerant circuit.
[0025]
The pipe 35 is supported so as to be suspended downward from the outlet hole 311, and the lower end portion of the pipe 35 protrudes into the discharge chamber 32 away from the inner wall surface of the front housing 31. Such a separation structure is effective in preventing the lubricating oil adhering to the inner wall surface of the front housing 31 from entering the cylinder of the pipe 35 by the action of the refrigerant gas flow. That is, the pipe 35 has a function as an oil separator that promotes separation of the lubricating oil from the refrigerant gas.
[0026]
As shown in FIGS. 1A and 1B, the discharge port 231 and the discharge chamber 32 are part of the gas flow path inside the compressor, and the discharge chamber 32 is a muffler that is part of the gas flow path. It is. The throttle channel 381 in the cylinder of the throttle unit 38 and the pressure recovery channel 391 in the cylinder of the diffuser unit 39 constitute a synthetic channel 40 provided on the downstream side of the discharge chamber 32 as a muffler with respect to the gas channel. To do. The pressure recovery channel 391 that constitutes the synthesis channel 40 provided on the downstream side of the discharge chamber 32 is provided on the downstream side of the throttle channel 381. The fixed scroll 11, the movable scroll 20, and the sealed spaces So and S1 constitute a pulsation source. The discharge pulsation is propagated to the external refrigerant circuit through the discharge chamber 32 and the synthetic flow path 40. The discharge chamber 32 and the throttle channel 381 reduce discharge pulsation. The discharge chamber 32 which is a muffler is disposed between the pulsation source and the synthesis flow path 40 with respect to the gas flow path.
[0027]
The following effects can be obtained in the first embodiment.
(1-1) In the throttle channel 381, the speed of the refrigerant gas increases and the pressure decreases. However, the refrigerant gas transferred from the throttle channel 381 to the pressure recovery channel 391 decreases the speed in the pressure recovery channel 391. Increase the pressure. That is, the pressure recovery flow path 391 recovers the pressure of the refrigerant gas that has passed through the throttle flow path 381. Since there is room for lowering the pressure in the throttle channel 381 as much as the pressure can be recovered in the pressure recovery channel 391, the passage cross-sectional area in the throttle channel 381 can be reduced to increase the discharge pulsation reduction effect.
[0028]
(1-2) The pipe 35 provided with the synthetic flow path 40 is fitted and fixed to the outlet hole 311 of the front housing 31. The fixing in this case can be performed by press-fitting or adhesion, for example. The arrangement of the pipe 35 with respect to the gas flow path (the outlet hole 311 in the present embodiment) having a diameter equal to or larger than the maximum outer diameter of the diffuser portion 39 is such that the outer diameter of the fitting portion 351 is changed to the gas flow. This is achieved by adjusting to the path diameter. Since the pipe 35 can be easily formed by pressing or the like, the size and shape of the pipe 35 in which the synthetic flow path 40 is provided depend on the shape of the gas flow path (outlet hole 311 in this embodiment). The throttle channel 381 and the pressure recovery channel 391 can be easily formed. Therefore, the inside of the pipe 35 is suitable as a place where the synthesis flow path 40 is formed.
[0029]
(1-3) The pipe 35 also functions as an oil separator. The configuration in which the synthetic flow path 40 is provided in the pipe 35 that functions as an oil separator can reduce the number of parts as compared with the case where a pipe dedicated to pulsation reduction is used, which contributes to cost reduction. Further, since the space occupied by the pipe dedicated to pulsation reduction is not necessary, an increase in the size of the compressor can be avoided.
[0030]
(1-4) In the pressure recovery in the pressure recovery flow path 391, it is important that the refrigerant gas flow flowing through the pressure recovery flow path 391 does not separate from the cylinder inner surface of the diffuser portion 39. The configuration in which the expansion angle θ1 in the pressure recovery flow path 391 is 20 ° or less is effective in preventing the separation of the refrigerant gas flow.
[0031]
(1-5) A compressor that generates discharge pulsation is a device that includes a muffler as part of a gas flow path. Such a compressor is suitable as an application target of the present invention.
Next, a second embodiment in which the present invention is embodied in a variable capacity compressor will be described with reference to FIGS. 2 (a) and 2 (b).
[0032]
As shown in FIG. 2A, the cylinder block 41, the front housing 42, and the rear housing 43 constitute an entire housing of a variable displacement compressor 44 as a device. A rotating shaft 45 is rotatably supported by the front housing 42 and the cylinder block 41 that form the control pressure chamber 421.
[0033]
A rotary support 46 is fixed to the rotary shaft 45 and a swash plate 47 is supported so as to be slidable and tiltable in the axial direction of the rotary shaft 45. The swash plate 47 can be tilted in the axial direction of the rotary shaft 45 and integrated with the rotary shaft 45 by a hinge mechanism comprising a guide hole 461 formed in the rotary support 46 and a guide pin 48 connected to the swash plate 47. Can be rotated.
[0034]
If the radius center part of the swash plate 47 moves to the rotation support body 46 side, the inclination angle of the swash plate 47 increases. The maximum inclination angle of the swash plate 47 is regulated by the contact between the rotary support 46 and the swash plate 47. The solid line position of the swash plate 47 in FIG. 2A indicates the maximum tilt angle state of the swash plate 47. When the radius center portion of the swash plate 47 moves toward the cylinder block 41, the inclination angle of the swash plate 47 decreases. The two-dot chain line position of the swash plate 47 in FIG. 2A indicates the minimum inclination state of the swash plate 47.
[0035]
Pistons 49 are accommodated in a plurality of cylinder bores 411 (only one is shown in the figure) penetrating the cylinder block 41. The rotational movement of the swash plate 47 is converted into the back-and-forth reciprocating movement of the piston 49 via the shoe 50, and the piston 49 reciprocates in the cylinder bore 411.
[0036]
A suction chamber 431 and a discharge chamber 432 are defined in the rear housing 43. A suction port 511 is formed in the valve plate 51 and the valve forming plate 53, and a discharge port 512 is formed in the valve plate 51 and the valve forming plate 52. A suction valve 521 is formed on the valve forming plate 52, and a discharge valve 531 is formed on the valve forming plate 53. The refrigerant gas in the suction chamber 431 flows into the cylinder bore 411 by pushing the suction valve 521 away from the suction port 511 by the backward movement of the piston 49 (movement from the right side to the left side in FIG. 2A). The refrigerant gas that has flowed into the cylinder bore 411 is discharged into the discharge chamber 432 by pushing the discharge valve 531 away from the discharge port 512 by the forward movement of the piston 49 [movement from the left side to the right side in FIG.
[0037]
The discharge chamber 432 and the control pressure chamber 421 are connected by a supply passage 54. Further, the control pressure chamber 421 and the suction chamber 431 are connected by a discharge passage 55. The refrigerant in the control pressure chamber 421 flows out to the suction chamber 431 through the discharge passage 55.
[0038]
An electromagnetic capacity control valve 56 is interposed on the supply passage 54. The capacity control valve 56 is in a valve-closed state where refrigerant cannot flow in the demagnetized state, and refrigerant supply from the discharge chamber 432 to the control pressure chamber 421 via the supply passage 54 is not performed. Since the refrigerant in the control pressure chamber 421 flows out to the suction chamber 431 through the discharge passage 55, the pressure in the control pressure chamber 421 decreases. Accordingly, the inclination angle of the swash plate 47 is increased and the discharge capacity is increased. The capacity control valve 56 is in a valve open state in which the refrigerant can flow by excitation, and the refrigerant is supplied from the discharge chamber 432 to the control pressure chamber 421 via the supply passage 54. Accordingly, the pressure in the control pressure chamber 421 increases, the inclination angle of the swash plate 47 decreases, and the discharge capacity decreases.
[0039]
A muffler 57 is formed on the peripheral surface of the cylinder block 41 and the peripheral surface of the front housing 42. A cylindrical portion 58 is provided in the muffler 57. The cylinder portion 58 is integrally formed with the cylinder block 41. The muffler 57 communicates with the discharge chamber 432 through the discharge passage 59. The muffler 57 communicates with the control pressure chamber 421 through the oil passage 60. A pipe 61 is fitted and fixed in the cylinder of the cylinder portion 58.
[0040]
As shown in FIG. 2B, the pipe 61 includes a nozzle part 62, a throttle part 63, and a diffuser part 64. The nozzle part 62, the throttle part 63, and the diffuser part 64 are arranged in series in this order from the muffler 57 to the outside of the compressor via the inside of the cylinder part 58. That is, the introduction path 621 in the cylinder of the nozzle part 62, the throttle flow path 631 in the cylinder of the throttle part 63, and the pressure recovery flow path 641 in the cylinder of the diffuser part 64 go in this order from the muffler 57 to the outside of the compressor. They are connected in series in the direction. The inner diameter of the nozzle part 62 is gradually reduced from the muffler 57 side toward the throttle part 63 side, and the introduction path 621 is connected to the throttle channel 631 on the small diameter part side.
[0041]
The inner diameter of the throttle part 63 is constant, and the inner diameter of the diffuser part 64 is gradually increased from the throttle part 63 side toward the outside of the compressor. An expansion angle θ1 (shown in FIG. 2B) of the diffuser portion 64 is set to 20 ° or less. The expansion angle θ2 (shown in FIG. 2B) of the nozzle portion 62 is larger than the expansion angle θ1 of the diffuser portion 64, but the inner peripheral surface of the nozzle portion 62 is shown in FIG. 2B. As indicated by an acute angle α, the cylinder portion 58 is bent and connected to the inner circumferential surface of the cylinder. That is, there is no level difference between the inner peripheral surface of the nozzle portion 62 and the inner peripheral surface of the cylinder portion 58 that is nearly perpendicular.
[0042]
When the refrigerant gas is discharged from the discharge passage 59 to the muffler 57, the refrigerant gas collides with the inner wall surface of the muffler 57, or the refrigerant gas changes its flow direction and goes into the cylinder of the cylinder portion 58. The contained lubricating oil is separated from the refrigerant gas. Further, since the refrigerant gas flow path from the muffler 57 to the cylinder of the cylinder part 58 is throttled in the cylinder of the cylinder part 58, it is difficult for the lubricating oil to enter the cylinder of the cylinder part 58. That is, the cylinder part 58 has a function as an oil separator that promotes separation of the lubricating oil from the refrigerant gas. The lubricating oil separated from the refrigerant gas is stored at the bottom of the muffler 57. The refrigerant gas in the muffler 57 goes out to the external refrigerant circuit (not shown) via the inside of the pipe 61.
[0043]
The discharge passage 59 and the muffler 57 are part of the gas flow path inside the variable displacement compressor 44. The throttle channel 631 in the cylinder of the throttle unit 63 and the pressure recovery channel 641 in the cylinder of the diffuser unit 64 constitute a synthetic channel 65 provided on the downstream side of the muffler 57 with respect to the gas channel. The pressure recovery flow path 641 constituting the synthesis flow path 65 provided on the downstream side of the muffler 57 is provided on the downstream side of the throttle flow path 631. The pipe 61 is provided in the cylinder of the cylinder portion 58 so that the refrigerant gas flows through the synthesis flow path 65.
[0044]
The piston 49 and the cylinder bore 411 constitute a pulsation source. The discharge pulsation propagates to the external refrigerant circuit via the discharge chamber 432, the discharge passage 59, the muffler 57, and the synthetic flow path 65. The muffler 57 and the throttle channel 631 reduce the discharge pulsation. The muffler 57 is disposed between the pulsation source and the synthesis channel 65 with respect to the gas channel.
[0045]
In the second embodiment, the same effect as the items (1-1), (1-4) and (1-5) in the first embodiment can be obtained. In order to fit and fix the pipe 61 in the cylinder of the cylinder part 58, the outer diameter of the pipe 61 may be set in accordance with the cylinder inner diameter of the cylinder part 58. The size and shape of the pipe 61 provided with the synthesis flow path 65 can be selected as appropriate according to the shape of the gas flow path pipe (in this embodiment, the cylinder portion 58). It is suitable as a formation place of the flow path 40.
[0046]
In the present embodiment, since the pipe 61 is accommodated in the cylinder of the cylinder portion 58, if there is a step close to a right angle on the inlet side of the pipe 61, this step provides a large flow resistance against the refrigerant gas flow. . Channel resistance results in pressure loss. Since the inner peripheral surface of the nozzle part 62 is connected to the cylinder inner peripheral surface of the cylinder part 58 at an acute angle, the flow path resistance to the refrigerant gas flowing into the pipe 61 is small.
[0047]
In addition, as shown in FIG. 3, the pressure recovery flow path 641A in which the cylinder inner peripheral surface of the diffuser portion 64A is smoothly connected to the cylinder inner peripheral surface of the throttle portion 63 is provided in the third tube 61A. Embodiments are possible. In this case, the expansion angle θ3 of the pressure recovery channel 641A constituting the synthetic channel 65A is an angle at the maximum diameter portion of the pressure recovery channel 641A as shown in FIG. The expansion angle θ3 of the pressure recovery channel 641A is set to 20 ° or less.
[0048]
Next, a fourth embodiment of FIG. 4 will be described. The same reference numerals are used for the same components as those in the first embodiment.
The front housing 31 is directly formed with a synthetic flow path 40 including a throttle flow path 381 and a pressure recovery flow path 391. In the fourth embodiment, the same effects as the items (1-1), (1-4), and (1-5) in the first embodiment can be obtained.
[0049]
Next, a fifth embodiment shown in FIGS. 5A, 5B, and 5C will be described. The same reference numerals are used for the same components as those in the first embodiment.
As shown in FIG. 5 (a), a cylindrical flow path forming body 66 is fitted and fixed in the inlet hole 28 formed in the peripheral wall of the rear housing 12 and the peripheral wall 111 of the fixed scroll 11. In the flow path forming body 66, a plurality of synthetic flow paths 67 are formed in parallel. Along with the revolution of the movable scroll 20, the refrigerant gas of the external refrigerant circuit (not shown) is introduced into the suction chamber 112 via the plurality of synthetic flow paths 67. The suction chamber 112 is a muffler that becomes a part of the gas flow path inside the compressor, and the synthetic flow path 67 is provided on the upstream side of the suction chamber 112 with respect to the gas flow.
[0050]
As shown in FIGS. 5A, 5 </ b> B, and 5 </ b> C, the synthetic channel 67 includes a pressure recovery channel 671, a throttle channel 672, and an introduction channel 673. The pressure recovery flow path 671 that constitutes the combined flow path 67 provided on the upstream side of the suction chamber 112, which is a muffler, is provided on the downstream side of the throttle path 672, and the throttle path 672 is connected to the introduction path 673. It is provided on the downstream side. The introduction path 673 gradually decreases in diameter from the external refrigerant circuit (external to the compressor) toward the throttle flow path 672, and the introduction path 673 is connected to the throttle flow path 672 on the small diameter side thereof. ing. The suction pulsation propagates to the external refrigerant circuit via the suction chamber 112 and the synthetic flow path 67. The suction chamber 112 and the throttle channel 672 reduce suction pulsation.
[0051]
In the throttle channel 672, the refrigerant gas speed increases and the pressure decreases. However, the refrigerant gas that has moved from the throttle channel 672 to the pressure recovery channel 671 decreases the speed and increases the pressure in the pressure recovery channel 671. That is, the pressure recovery flow path 671 recovers the pressure of the refrigerant gas that has passed through the throttle flow path 381. Since there is room for lowering the pressure in the throttle channel 672 as much as the pressure can be recovered in the pressure recovery channel 671, the passage cross-sectional area in the throttle channel 672 can be reduced to increase the suction pulsation reduction effect.
[0052]
If a single synthetic flow path is used in the inlet hole 28, the difference in diameter between the throttle flow path and the gas flow path becomes large, so that the length of the pressure recovery flow path needs to be increased. If a plurality of synthesis channels 67 are provided in parallel, the passage cross-sectional area of each throttle channel 672 can be reduced, so that the length of the pressure recovery channel 671 can be shortened. The shortening of the pressure recovery channel 671 leads to the shortening of the synthesis channel 67. The shortening of the synthesis channel 67 contributes to the miniaturization of the channel formation body 66. That is, the configuration in which the plurality of synthetic flow paths 67 are provided in parallel is advantageous for suppressing the increase in the size of the compressor to which the flow path forming body 66 is attached.
[0053]
In the present invention, the following embodiments are also possible.
(1) The present invention may be applied to a compressor other than a scroll compressor and a variable capacity compressor (for example, a swash plate compressor, a vane compressor, etc.).
[0054]
(2) In the exhaust system attached to the vehicle engine, the present invention may be applied to a device provided with a muffler as a part of a gas flow path. In this case, it is only necessary to provide a synthetic flow path in which the throttle flow path and the pressure recovery flow path are combined in series on the downstream side of the muffler with respect to the gas flow path.
[0055]
(3) The pipe may be deformed by applying pressure to the outer peripheral surface of the pipe, and the throttle flow path and the pressure recovery flow path may be formed in the pipe cylinder by this pressure deformation.
The technical idea that can be grasped from the embodiment described above will be described below.
[0056]
[1] A pulsation reducing structure in an apparatus having a gas flow path according to claim 2, wherein the pipe projects into the muffler.
[2] The pulsation reducing structure in a device having a gas flow path according to any one of claims 1 to 5, and [1], wherein the expansion angle of the pressure recovery flow path is 20 ° or less.
[0057]
[3] A flow path forming body including a plurality of combined flow paths in which a throttle flow path and a pressure recovery flow path are combined in series.
[0058]
【The invention's effect】
As described above in detail, the present invention has an excellent effect that a sufficient pulsation reducing effect can be obtained in a device having a gas flow path and a pulsation reducing structure capable of suppressing pressure loss can be provided.
[Brief description of the drawings]
FIG. 1 shows a first embodiment, and FIG. 1 (a) is a side sectional view of the whole compressor. (B) is a principal part expanded side sectional view.
FIG. 2 shows a second embodiment, and (a) is a side sectional view of the whole compressor. (B) is a principal part expanded side sectional view.
FIG. 3 is an enlarged cross-sectional side view of a main part showing a third embodiment.
FIG. 4 is an enlarged cross-sectional side view of a main part showing a fourth embodiment.
FIG. 5 shows a fifth embodiment, wherein (a) is an enlarged side sectional view of a main part. FIG. 6B is an end view of the flow path forming body 66. (C) is CC sectional view taken on the line of (b).
[Explanation of symbols]
10: A scroll compressor as a device. 11 ... A fixed scroll constituting a pulsation source. 112 ... Suction chamber as a muffler. 20: A movable scroll constituting a pulsation source. 231: Discharge port that is part of the gas flow path. 32: Discharge chamber as a muffler. 35, 61, 61A ... pipe. 381,631,672 ... throttle channel. 391, 641, 641A, 671 ... pressure recovery flow path. 40, 65, 65A, 67 ... synthetic flow path. 411 ... Cylinder bore constituting the pulsation source. 44 ... Variable capacity compressor as equipment. 49 ... Piston constituting pulsation source. 57 ... Muffler. 59 ... A discharge passage which is a part of the gas flow path. 621, 673... An introduction path in which the small diameter side is connected to the throttle channel. So, S1 ... Sealed space constituting the pulsation source.

Claims (5)

In a device provided with a muffler as a part of a gas flow path for reducing pulsation spreading from a pulsation source,
A synthetic flow path is provided on the upstream side or downstream side of the muffler with respect to the gas flow path, and a combined flow path and a pressure recovery flow path are connected in series, and the downstream side of the throttle flow path with respect to the gas flow path. A pulsation reducing structure in a device having a gas flow path, wherein the pressure recovery flow path is provided, and the muffler is disposed between the pulsation source and the synthetic flow path with respect to the gas flow path. The gas flow path according to claim 1, wherein the synthesis flow path is provided in a pipe cylinder, and the pipe is disposed in the gas flow path so that the gas in the gas flow path flows through the synthesis flow path. Pulsation reduction structure in equipment equipped with The pulsation reducing structure in an apparatus provided with the gas flow path according to claim 1, wherein a plurality of the synthetic flow paths are provided in parallel. 4. The tapered passage according to claim 2, wherein a tapered introduction path is connected in series to the throttle passage, and a small diameter portion side of the tapered introduction path is connected to the throttle passage. Pulsation reduction structure in equipment with gas flow path. The pulsation reducing structure in a device having a gas flow path according to any one of claims 1 to 4, wherein the device is a compressor.

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