JP2008031866A - Compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compressor which releases residual gas from an early stage after a discharge stroke is completed, regardless of layout of an intake passage of a rotary valve. <P>SOLUTION: The rotary valve 71 has a releasing passage 71e releasing high-pressure residual gas that can not be discharged at the discharge stroke from a cylinder bore B<SB>1</SB>during the early stage of an intake stroke to other cylinder bores B<SB>3</SB>, B<SB>4</SB>lower in pressure than the cylinder bore B<SB>1</SB>. The releasing passage 71e has an inlet 71f, a first outlet 71g, a second outlet 71h, and a communicating part 71k communicating with them. In a period where the inlet 71f of the releasing passage 71e communicates with the cylinder bore B<SB>1</SB>during the early stage of the intake stroke, the second outlet 71h communicates with a cylinder bore B<SB>4</SB>opposed to the cylinder bore B<SB>4</SB>by 180° after the first outlet 71g communicates with a cylinder bore B<SB>3</SB>previous to, in a rotational direction, the cylinder bore B<SB>4</SB>opposed to the cylinder bore B<SB>1</SB>by 180°. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a compressor.

  For example, Patent Document 1 discloses a compressor in which a piston is housed in a plurality of cylinder bores arranged around a rotation shaft, and the piston is reciprocated in conjunction with the rotation of the rotation shaft. In this compressor, a suction passage for introducing a refrigerant gas into a compression chamber defined in a cylinder bore by a piston is formed on a rotary valve, and the compression chamber and the suction passage are connected in synchronization with the reciprocation of the piston. A rotary valve is provided in order.

  Further, the rotary valve is provided with a discharge passage, and by this discharge passage, the high-pressure residual gas remaining in the compression chamber near the top dead center timing of the piston is in the state near the bottom dead center timing. It can be discharged to other compression chambers.

According to such a configuration, since the residual gas is reduced, that is, the amount of the high-pressure residual gas that is re-expanded in the intake stroke is reduced, the refrigerant gas can be sucked into the more compression chambers. Thus, the suction efficiency is improved and the compression performance of the compressor is improved.
Japanese Patent No. 3079743 Japanese Patent No. 3077741

  Normally, the high-pressure residual gas remaining in the cylinder bore where the piston is at top dead center (cylinder bore at the time of the discharge stroke = cylinder bore at the start of the intake stroke) is transferred to the cylinder bore (at the end of the intake stroke) which is 180 ° opposite to the cylinder bore. If the cylinder bore is released to the cylinder bore at the start of the discharge stroke), the pressure difference between the two cylinder bores is the largest, so it seems to be efficient.

  However, depending on the layout of the intake passage of the rotary valve, there are cases where the residual gas cannot escape from the cylinder bore where the piston is located at the top dead center position to the cylinder bore which is 180 ° opposite to the cylinder bore. For example, as disclosed in Patent Document 2, the case where the end timing of communication between each cylinder bore and the suction passage of the rotary valve is set later than the bottom dead center timing of the piston in each cylinder bore is an example. is there. In such a case, since the cylinder bore is still in communication with the suction passage at an early stage immediately after the end of the suction stroke, the cylinder bore on the opposite side of the cylinder bore by 180 ° to the cylinder bore (that is, the cylinder bore at the early stage immediately after the end of the discharge stroke). ) Can not release the residual pressure.

  The present invention has been made on the basis of such a conventional technique. It is an object of the present invention to provide a compressor that allows residual gas to escape from an early stage after the end of the discharge stroke, regardless of the layout of the suction passage of the rotary valve. To do.

  According to the first aspect of the present invention, an even number of four or more cylinder bores provided at equal intervals in the circumferential direction around the drive shaft, and the suction holes formed in the partition walls, which are defined by the cylinder bores and the partition walls. A suction chamber that communicates with the cylinder bore through, a discharge chamber that is partitioned by the cylinder bore and the partition wall and communicates with the cylinder bore through a discharge hole formed in the partition wall, and a piston that is reciprocally disposed in each cylinder bore; The pistons in the cylinder bores reciprocate sequentially in conjunction with the rotation of the drive shaft, whereby a suction stroke and a discharge stroke are alternately performed in each cylinder bore. In the suction stroke, the suction stroke Fluid is sucked into the cylinder bore from the suction chamber through a hole, and the fluid is compressed in the cylinder bore in the discharge stroke. A compressor in which the compressed fluid is discharged from the cylinder bore to the discharge chamber through the discharge hole, and is arranged to be slidable and slidable so as to close the suction hole with respect to the partition wall, and is rotated synchronously with the drive shaft A rotary valve coupled to the drive shaft, the rotary valve having a suction passage that opens the suction hole of the cylinder bore in the suction stroke and communicates the cylinder bore with the suction chamber, and discharges There is an escape passage for letting out the high pressure residual fluid that has not been discharged in the stroke from the cylinder bore in the initial stage of the suction stroke to another cylinder bore having a lower pressure than the cylinder bore, and the escape passage overlaps with the suction hole. An inlet and a first outlet and a second outlet provided on the upper side, and a communication portion that communicates the inlet and the outlet. While the inlet of the escape passage communicates with the cylinder bore in the initial stage of the entry stroke, A: the first outlet communicates with the cylinder bore one rotation direction before the cylinder bore on the 180 ° opposite side of the cylinder bore. C: Next, the second outlet communicates with a cylinder bore on the opposite side of the cylinder bore by 180 °.

  Invention of Claim 2 is a compressor of Claim 1, Comprising: The A period and the C period partially overlap, and the A period and the C period are continuous without interruption. It is characterized by.

  According to the first aspect of the present invention, the second outlet communicates with a cylinder bore on the opposite side of the cylinder bore by 180 ° during a period in which the inlet of the escape passage communicates with the cylinder bore in the initial stage of the intake stroke. Before the operation, the first outlet communicates with the cylinder bore one rotation direction before the cylinder bore on the opposite side of 180 ° of the cylinder bore.

  In this way, by using the cylinder bore one rotation direction before the cylinder bore 180 ° opposite to the cylinder bore in the initial stage of the suction stroke, immediately after the end of the discharge stroke (= immediately after the start of the suction stroke) regardless of the layout of the suction passage. From this early stage, high-pressure residual fluid can be released. As a result, regardless of the layout of the suction passages, the suction efficiency can be maintained high, and the compression performance of the compressor can be maintained high.

  According to invention of Claim 2, it is a compressor of Claim 1, Comprising: The said A period and the said C period overlap, and the said A period and the said C period are continued without interruption. Therefore, the residual pressure can be released without interruption, and the suction performance can be further improved.

  In this specification, the suction stroke refers to the period during which the piston moves from the top dead center position to the bottom dead center position, and the discharge stroke refers to the piston moving from the bottom dead center position to the top dead center position. The end of the discharge stroke and the start of the suction stroke are when the piston is at the top dead center, and the end of the suction stroke and the start of the discharge stroke are when the piston is at the bottom dead center. Say.

  A compressor according to an embodiment of the present invention will be described with reference to the drawings.

(First embodiment)
Hereinafter, the compressor according to the first embodiment will be described with reference to FIGS.

  FIG. 1 is a cross-sectional view of the compressor according to the first embodiment, and FIG. 2 is a cross-sectional view taken along the line ZZ in FIG. The compressor 1 of this embodiment is a swash plate type variable capacity compressor as shown in FIG. The compressor 1 includes a cylinder block 2 (see FIG. 2) having a plurality of cylinder bores Bj (j = 1 to 6 in this example) arranged at equal intervals in the circumferential direction, and a front end surface of the cylinder block 2 The front head 4 that forms the crank chamber 5 that is joined to the cylinder bore Bj and is connected to the rear end face of the cylinder block 2 via the valve plate 9, and the suction chamber 7 and the discharge chamber 8 are formed inside the front head 4. And a rear head 6. The cylinder block 2, the front head 4 and the rear head 6 are fastened and fixed by a plurality of through bolts 13 to constitute a housing of the entire compressor.

  A gasket 53 is interposed between the valve plate 9 and the rear head 6 so that the airtightness of the suction chamber 7 and the discharge chamber 8 is maintained. Further, a gasket 54 is interposed between the valve plate 9 and the cylinder block 2 to maintain the sealing performance of the cylinder bore Bj.

  The valve plate 9 is formed in a disc shape, and is formed to penetrate at a position corresponding to each cylinder bore Bj, and communicates the cylinder bore bj and the suction chamber 7 (in this example, j = 1 to 6), Discharge holes 12j (in this example, j = 1 to 6) that are formed so as to penetrate the cylinder bore Bj and communicate with the cylinder bore Bj and the discharge chamber 8 are provided.

  As will be described in detail later, on the rear head 6 side of the valve plate 9, a suction valve mechanism 70 for opening and closing the suction hole 11j and a discharge valve mechanism 60 for opening and closing the discharge hole 12j are provided.

  A drive shaft 10 is pivotally supported via radial bearings 15 and 19 in the central through holes 14 and 18 at the centers of the cylinder block 2 and the front head 4, so that the drive shaft 10 can freely rotate in the crank chamber 5. Yes.

  A thrust bearing 20 is interposed between the front end surface of the rotor 21 fixed to the drive shaft 10 in the crank chamber 5 and the inner wall surface of the front head 4, and is fixed to the central through hole 14 of the cylinder block 2. A thrust bearing 16 is interposed between the adjusting screw 17 and the stepped surface formed on the drive shaft 10. Thereby, the movement to the axial direction of the drive shaft 10 is controlled.

  A conversion mechanism that converts the rotation of the drive shaft 10 into a reciprocating motion of the piston Pj (j = 1 to 6 in this example) is provided in the crank chamber 5. The conversion mechanism includes a rotor 21 as a rotary member fixed to the drive shaft 10, a rotary swash plate 24 that is slidable and tiltable in the axial direction with respect to the drive shaft 10, and the rotor 21 and the rotary tilt. A coupling mechanism 40 that couples the plate 24 and transmits the rotational torque of the rotor 21 to the rotary swash plate 24 while allowing fluctuations in the tilt angle of the rotary swash plate 24. Each piston Pj is connected to the outer peripheral portion of the rotary swash plate 24 via a pair of hemispherical piston shoes 30, 30, and when the rotary swash plate 24 rotates, the piston Pj corresponds to the inclination angle of the rotary swash plate 24. Reciprocates in the cylinder bore Bj. By the reciprocating motion of the piston Pj, the refrigerant in the suction chamber 7 is sucked into the cylinder bore Bj through the suction hole 11j of the valve plate 9 and then compressed in the cylinder bore Bj, and the compressed refrigerant is discharged into the discharge hole of the valve plate 9 It is discharged into the discharge chamber 8 through 12j.

  When the rotating swash plate 24 moves close to the cylinder block 2 against the return spring 52, the inclination angle of the rotating swash plate 24 decreases, while the rotating swash plate 24 moves from the cylinder block 2 against the disstroke spring 51. When it moves away, the inclination angle of the rotary swash plate 24 increases.

Control of variable capacity In order to change the discharge capacity of the refrigerant, the piston stroke is changed by changing the inclination angle of the rotary swash plate 24. More specifically, the piston stroke is changed by changing the tilt angle of the rotary swash plate 24 by the differential pressure (pressure balance) between the crank chamber pressure Pc on the rear surface side of the piston Pj and the suction chamber pressure Ps on the front surface side of the piston Pj. Let Therefore, this variable capacity compressor is provided with a pressure control mechanism. The pressure control mechanism includes an extraction passage (not shown) that connects the crank chamber 5 and the suction chamber 7, an air supply passage (not shown) that connects the crank chamber 5 and the discharge chamber 8, and the air supply passage. , And a control valve 33 that controls opening and closing of the air supply passage.

  When the air supply passage is opened by the control valve 33, a high-pressure refrigerant gas flows from the discharge chamber 8 through the air supply passage to the crank chamber 5, thereby increasing the pressure in the crank chamber 5. When the pressure in the crank chamber 5 rises, the rotary swash plate 24 moves closer to the cylinder block 2 and its inclination angle decreases, so that the piston stroke becomes smaller and the discharge amount decreases.

  On the other hand, when the air supply passage is closed by the control valve 33, the refrigerant gas is constantly discharged into the suction chamber 7 through the extraction passage into the crank chamber 5, so that the pressure difference between the suction chamber 7 and the crank chamber 5 gradually disappears. Equalize pressure. Then, the rotary swash plate 24 moves in a direction away from the cylinder block 2 and its inclination angle increases, the piston stroke increases, and the discharge amount increases.

Next, the valve mechanisms 60 and 70 will be described.

First, the discharge valve mechanism 60 will be described with reference to FIG. The discharge valve mechanism 60 includes a discharge valve plate 61. As shown in FIG. 1, the discharge valve plate 61 is sandwiched between the valve plate 9 and the rear head 6. The discharge valve plate 61 is formed of an elastic flexible thin plate (for example, a metal thin plate), and has a reed valve portion 63 at a position corresponding to the discharge hole 12j. The reed valve portion 63 closes the discharge hole 12j when the inside of the cylinder bore Bj is equal to or lower than a predetermined pressure, and opens the discharge hole 12j when the inside of the cylinder bore Bj exceeds the predetermined pressure. That is, the reed valve portion 63 closes the discharge hole 12j during the intake stroke and the compression stroke, and opens the discharge hole 12j in the discharge stroke at the final stage of the compression stroke. The open limit position of the reed valve portion 63 is regulated by a stopper portion 65 provided on the gasket 53.
Next, the suction valve mechanism 70 will be described in more detail with reference to FIGS.

  The intake valve mechanism 70 includes a rotary valve 71, a stopper 73, and a coil spring 75 as a spring member. The rotary valve 71, the stopper 73, and the coil spring 75 are all disposed in the suction chamber 7, as shown in FIG.

  The rotary valve 71 is formed in a substantially disk shape, and a central through-hole 71b is formed at the center thereof. An axial end portion 10 a of the drive shaft 10 that extends through the central through-hole 9 c of the valve plate 9 to the suction chamber 7 is attached to the central through-hole 71 b of the rotary valve 71. The central through hole 71b of the rotary valve 71 and the axial end portion 10a of the drive shaft 10 are formed in the same non-circular shape (hexagonal in this example) as shown in FIG. Is rotated integrally with the drive shaft 10 so as to be slidable in the axial direction.

  The stopper 73 is restricted from moving in the axial direction by a bolt 77 as a fastening means at the axial end 10 a of the drive shaft 10. A pair of arms 73 d project from the stopper 73 toward the rotary valve 71, and the pair of arms 73 d are connected to the rotary valve 71, whereby the stopper 73 rotates integrally with the rotary valve 71. A coil spring 75 is compressed and held between the stopper 73 and the rotary valve 71, so that the rotary valve 71 is always in close contact with the valve plate 9 while being biased. Yes.

  As shown in FIG. 2, the rotary valve 71 is formed with a long-hole-shaped suction passage 71 c extending in an arc shape. When the rotary valve 71 rotates, the suction passage 71 c of the rotary valve 71 is connected to the valve plate 9. The suction holes 11j are sequentially overlapped with the suction holes 11j, and the suction holes 11j are sequentially opened (see FIGS. 2 to 6).

  The opening timing of the suction hole 11j by the suction passage 71c is set so as to be synchronized with the suction stroke of the piston Pj.

In the state shown in FIGS. 1 and 2 is in the top dead center the piston P ₁ of the cylinder bore B _1, located on the piston P ₄ is the bottom dead center of the cylinder bore B ₄ which is in 180 ° rotational symmetry position, the top dead center state The cylinder bores B ₂ and B ₃ between the cylinder bore B ₁ at the bottom and the cylinder bore B ₄ at the bottom dead center are in the compression stroke, and the cylinder bore B ₄ at the bottom dead center and the cylinder bore at the top dead center Cylinder bores B ₅ and B ₆ between B ₁ are in the intake stroke.

When in the state shown in such Figures 1 and 2, the suction passage 71c is without communicating the suction hole 11 ₁ of the cylinder bore B ₁ in the top dead center state, suction of the cylinder bore B _5, B ₆ in the suction phase It communicates with the holes 11 ₁ and 11 ₄ and also communicates with the suction hole 11 ₁ of the cylinder bore B _{4 in} the bottom dead center state.

  That is, the valve opening start timing (see FIG. 5) of the suction hole 11j by the suction passage 71c is delayed from the top dead center timing (FIG. 2) of the piston Pj in each cylinder bore Bj. The valve opening end timing (FIG. 4) is set later than the bottom dead center timing (FIG. 2) of the piston Pj in each cylinder bore Bj.

Specifically, the cylinder bore B ₁ and the cylinder bore B ₄ will be described as an example. In the cylinder bore B ₁ , the piston P ₁ is at the top dead center in the state shown in FIG. 1, and after that, the suction hole by the suction passage 71 c in the state shown in FIG. 11j is started. Further, in the cylinder bore B _4, in a state BDC the piston P ₄ are in the Figure 1, behind which in the state of FIG. 5 nearing the opening end timing of the suction hole 11j by inhalation passage 71c.

  As described above, when the valve opening end timing of the suction hole 11j by the suction passage 71c is set later than the bottom dead center timing of the piston Pj in each cylinder bore Bj, the suction stroke in each cylinder bore Bj (the piston Pj is dead top). Is drawn into the momentum (inertia) of the flow of the suction gas sucked in (from the point to the bottom dead center), and the discharge stroke initial stage after the suction stroke (the piston Pj moves from the bottom dead center toward the top dead center). The intake gas is taken into the cylinder bore Bj even at the stage of starting movement). As a result, the amount of suction increases, the suction efficiency improves, and the compression efficiency of the compressor 1 improves.

Residual pressure relief structure Next, the residual pressure relief structure will be described with reference to FIGS.

  The rotary valve 71 is provided with a relief passage 71e as shown in FIGS.

  The escape passage 71e is configured as a groove recessed in the surface of the rotary valve 71, and includes an inlet 71f, two outlets 71g and 71h, and a communication portion 71k that communicates the inlet 71f and the outlets 71g and 71h. Configured. The inlet 71f and the outlets 71g and 71h are provided on a rotation track overlapping the suction hole 11j, and sequentially communicate with the suction hole 11j when the rotary valve 71 rotates. The communication portion 71k is provided at a position deviating from the rotation path and does not overlap with the suction hole 11j.

  The escape passage 71e allows the high-pressure residual fluid remaining in the cylinder bore Bj in the initial stage of the suction stroke to be discharged during the discharge stroke to another cylinder bore Bj having a lower pressure than the cylinder bore Bj.

Figures 2-6 are from the start the intake stroke of the cylinder bore _{B 1} (FIG. 2), immediately before (FIG. 6) to the cylinder bore _{B 1} is communicated with the suction path 71c, the relief of the rotary valve 71 the passage 71e and the cylinder bores Bj It is the figure which showed how and communicate.

As shown in FIG. 2 to FIG. 6, an escape passage inlet 71 f is provided with respect to the cylinder bore B _{1 in the} initial stage of the intake stroke (in this example, the period after the discharge stroke ends and before the intake passage 71 c communicates). In the communicating period (FIGS. 3 to 5), first, as shown in FIG. 3, the first outlet 71 g is one rotation direction before the cylinder bore B ₄ on the opposite side of the cylinder bore B ₁ by 180 °. communicating with the cylinder bore _{B 3} of. Next, as shown in FIG. 5, the second outlet 71h communicates with the cylinder bore B ₄ on the opposite side of the cylinder bore B ₁ by 180 °. Here, when the first outlet 71g is a period for communicating with the cylinder bore B ₃ and A period (Fig. 3), the period during which the second outlet 71h communicates with the cylinder bore B ₄ and C periods (Figure 5), period A as shown in Figure 4 between (Fig. 3) and C periods (Figure 5), the first outlet 71g communicates with the suction hole 11 ₃ of the cylinder bore _{B 3,} the second outlet 71h is cylinder bore B B period for communicating with the suction hole 11 ₄ of _4, is a moment exists.

7 and 8 are views in which the pressure curves in the cylinder bore B ₁ , the cylinder bore B ₃ , and the cylinder bore B ₄ are superimposed, and in the figure, the solid line is a line indicating the pressure curve in the cylinder bore B ₁ , and is a one-dot chain line. Is a line showing a pressure curve in the cylinder bore B ₃ , and a two-dot chain line is a line showing a pressure curve in the cylinder bore B ₄ .

7 and 8, θ indicates the rotation angle of the rotary valve. In FIGS. 7 and 8, the reference rotation angles θ = 0 ° and 360 ° are shown, and the cylinder bore B ₁ is at the top dead center. state (state where the piston P ₁ of the cylinder bore B ₁ is at the top dead center position), i.e., the cylinder bore B ₄ is bottom dead center state (state in which the piston P ₄ is at the bottom dead center position in the cylinder bore B ₄₎ It is shown as

Figure 8 is particularly the cylinder bore B ₁ is shows an enlarged suction stroke initial stage (θ = 0 ° ~30 near °). Arrows in Figure 8, the high pressure residual gas remaining in the cylinder bore B ₁ is a diagram illustrating a manner in which flows into the cylinder bore B ₃ and B _4. The A period, B period, and C period in FIG. 8 correspond to the above-described A period (FIG. 3), B period (FIG. 4), and C period (FIG. 5).

Thus, as is apparent from FIG. 8, in the present embodiment, in the cylinder bore B ₁ in the initial stage of the suction stroke, the second outlet 71h communicates with the cylinder bore B ₄ on the opposite side of the cylinder bore B ₁ by 180 °. prior period (Fig. 5), the first outlet 71g is, a period that communicates with the direction of rotation immediately preceding the cylinder bore _{B 3} from the cylinder bore _{B 4} of 180 ° opposite side of the cylinder bore _{B 1} (FIG. 3) is is there. Therefore, with respect to the cylinder bore _{B 1} of the suction stroke initial stage (A through C period), by using the 180 ° opposite the cylinder bore _{B 4} rotational direction immediately preceding the cylinder bore _{B 3} from the arrangement layout of the suction passage 71c Regardless, the high-pressure residual fluid can be released from an early stage immediately after the end of the discharge stroke (= immediately after the start of the suction stroke), the suction efficiency can be kept high, and the compression performance of the compressor can be kept high.

Although described the cylinder bore _{B 1} in Figures 2-6 as an example, it will communicate the release path 71e also in the cylinder bore of the cylinder bore _B 2 .about.B _6.

Effects Next, effects of the present embodiment are listed.

  (1) The compressor 1 according to this embodiment includes an even number of four or more cylinder bores Bj provided around the drive shaft 10 at equal intervals in the circumferential direction, the cylinder bores Bj, and the partition walls (in this example, the valve plate 9 ) And a suction chamber 7 that communicates with the cylinder bore Bj through a suction hole 11j formed in the partition, and is defined by the cylinder bore Bj and the partition (in this example, the valve plate 9) and is formed in the partition. A discharge chamber 8 communicating with the cylinder bore Bj through the discharge hole 12j, a piston Pj disposed reciprocally in each cylinder bore Bj, and a conversion mechanism for converting the rotation of the drive shaft 10 into the reciprocation of the piston Pj. 21, 24, 40, 30, and in conjunction with the rotation of the drive shaft 10, pistons Pj in the cylinder bores Bj By sequentially reciprocating, a suction stroke and a discharge stroke are alternately performed in each cylinder bore Bj. In the suction stroke, fluid is sucked into the cylinder bore Bj from the suction chamber 7 through the suction hole 11j. In the discharge stroke, the compressor 1 discharges the compressed fluid from the cylinder bore Bj to the discharge chamber 8 through the discharge hole 12j after the fluid is compressed in the cylinder bore Bj. A rotary valve 71 is provided so as to be rotatable and slidable so as to close the suction hole 11j with respect to the partition wall and coupled to the drive shaft 10 so as to rotate synchronously with the drive shaft 10. The rotary valve 71 has a suction passage 71c that opens the suction hole 11j of the cylinder bore Bj in the suction stroke and communicates the cylinder bore Bj with the suction chamber 7. Further, the rotary valve 71 has a release passage 71e for letting the high-pressure residual fluid remaining without being discharged in the discharge stroke from the cylinder bore Bj in the initial stage of the intake stroke to another cylinder bore Bj having a lower pressure than the cylinder bore Bj. The escape passage 71e is separated from the inlet 71f, the first outlet 71g and the second outlet 71h provided on the rotation track overlapping the suction hole 11j, and the rotation track overlapping the suction hole 11j. A communication portion 71k communicating with the outlet.

  In the period in which the inlet 71f of the escape passage 71e communicates with the cylinder bore Bj in the initial stage of the suction stroke, A: the cylinder bore Bj 180 ° opposite to the cylinder bore Bj. It communicates with the cylinder bore Bj one rotation direction before, and then C: the second outlet 71h communicates with the cylinder bore Bj 180 ° opposite to the cylinder bore Bj.

That is, if explaining the cylinder bore B ₁ as an example, as shown in FIGS. 3-5, the cylinder bore B ₁ of the suction stroke initial stage (period before communicating with and suction passage 71c after completion of the discharge stroke in this example), in a period when the inlet 71f is communicated with the release path 71e (FIGS. 3-5), first, a period: first outlet 71g has one rotational direction than the cylinder bore _{B 4} of 180 ° opposite side of the cylinder bore _{B 1} before The cylinder bore B ₃ communicates with the cylinder bore B _3, and then the C period: the second outlet 71 h communicates with the cylinder bore B ₄ on the opposite side of the cylinder bore B ₁ by 180 °.

As described above, in the present embodiment, the cylinder bore B ₃ that is one rotation direction before the cylinder bore B _{4 that} is 180 ° opposite to the cylinder bore B _{1 in} the initial stage of the intake stroke is used regardless of the layout of the intake passage 71c. From the early stage immediately after the end of the discharge stroke (= immediately after the start of the suction stroke), the high-pressure residual fluid can be released, the suction efficiency can be kept high, and the compression performance of the compressor can be kept high.

Although described the cylinder bore _{B 1} as an example, it will communicate the release path 71e also in the cylinder bore of the cylinder bore _B 2 .about.B _6.

  (2) Particularly in the present embodiment, the layout of the suction passage 71c is set such that the valve opening end timing of the suction hole 11j by the suction passage 71c is delayed from the bottom dead center timing of the piston Pj in each cylinder bore Bj. .

In other words, the cylinder bore B ₁ and the cylinder bore B ₄ that are 180 ° opposite to each other will be described as an example, and the suction is performed after the bottom dead center timing (FIG. 2) of the piston P ₄ in the cylinder bore B ₄ shown in FIG. opening end timing of the suction hole 11 ₄ of the cylinder bore _{B 4} by passage 71c (Fig. 4) is set.

  Therefore, in each cylinder bore Bj, it is drawn into the momentum (inertia) of the flow of the suction gas sucked during the suction stroke (while the piston Pj moves from the top dead center to the bottom dead center), and after the suction stroke (initial stage of the discharge stroke) (Stage = stage where piston Pj starts to move from bottom dead center to top dead center), intake gas is taken into cylinder bore Bj. As a result, the amount of suction increases, the suction efficiency improves, and the compression efficiency of the compressor 1 improves.

In such a structure, the residual gas cannot escape from the cylinder bore Bj where the piston Pj is at the top dead center position to the cylinder bore Bj which is 180 ° opposite to the cylinder bore. In other words, the cylinder bore B ₁ and the cylinder bore B ₄ that are positioned 180 ° opposite to each other will be described as an example. From the cylinder bore B ₁ (FIG. 3) immediately after the top dead center, the cylinder bore B that is 180 ° opposite to the cylinder bore B ₁ . to B _4, a structure that does not Nigase residual gas. Although not described with reference to the drawings, the same applies to the cylinder bore B ₂ and the cylinder bore B ₅ that are 180 ° opposite to each other, and to the cylinder bore B ₁ and the cylinder bore B ₄ that are 180 ° opposite to each other. In the state immediately after the top dead center of the piston, the residual gas cannot flow. Therefore, the effect (1) is exhibited effectively.

  (3) In the present embodiment, the A period and the C period partially overlap, and the A period and the C period are continuous without interruption. Therefore, since the residual pressure can be released without interruption, the suction performance can be further improved.

  (4) Further, the compressor 1 of the present embodiment includes a drive shaft 10 that extends to the suction chamber 7 side through a through-hole 9 c that is formed through the valve plate 9 and is rotatable, and a drive shaft in the suction chamber 7. 10, a substantially plate-like rotary valve 71 that rotates integrally with the drive shaft 10 and opens and closes the suction hole 11 j of the valve plate 9 with the integral rotation with the drive shaft 10. And a stopper 73 mounted in a state in which the movement in the axial direction is restricted, and the rotary valve 71 is mounted in a state slidable in the axial direction with respect to the drive shaft 10 and is held by the stopper 73. The valve plate 9 is urged by a coil spring 75 as a spring member.

  That is, the rotary valve 71 is slidable in the axial direction with respect to the drive shaft 10, rotates integrally with the drive shaft 10, and is biased toward the valve plate 9 by the spring member 75. Therefore, the rotary valve 71 is in close contact with the valve plate 9, so that the high-pressure compressed medium compressed in the cylinder bore Bj becomes the gap between the cylinder bore Bj → the suction hole 11 j → the valve plate 9 and the rotary valve 71 → Leakage into the suction chamber 7 is reduced, and compression efficiency is improved. Further, when the pressure in the cylinder bore Bj becomes excessive, the rotary valve 71 can be separated from the valve plate 9 and the excess high-pressure medium in the cylinder bore Bj can be released to the suction chamber 7. That is, the compressor 1 of the present embodiment includes a safety function when the inside of the cylinder bore Bj is in an abnormally high pressure state.

  Further, unlike the prior art (for example, Japanese Patent Laid-Open No. 8-144946, FIGS. 3, 6, 9, 12 and the like), the coil spring 75 is not in contact with the rear head 6, so that the vibration of the rotary valve 71 is transmitted through the coil spring 75. Thus, transmission to the rear head 6 is prevented. Thereby, in the compressor 1 of this embodiment, sound vibration property improves.

  Further, since the stopper 73 of the coil spring 75 rotates integrally with the rotary valve 71, the coil spring and the rotary bubble are not provided as in the prior art (for example, Japanese Patent Laid-Open No. 8-144946, FIGS. 3, 6, 9, 12). It is not necessary to arrange a thrust bearing between the coil spring and the stopper. Therefore, an expensive thrust bearing is not necessary, and the cost can be reduced.

  Hereinafter, modifications of the first embodiment will be described. In the following description of the modified examples and other embodiments, the same reference numerals are given to the same configurations as those in the first embodiment, and the description of the configurations and the operational effects thereof is omitted.

First modification
FIG. 10 shows a first modification of the rotary valve of the first embodiment.

  In the rotary valve 71 of the first embodiment, the communication part 71k of the escape passage 71e is formed in a groove shape on the surface of the rotary valve 71 (see FIG. 9), but the first of the rotary valve 71 shown in FIG. In the first modification, the communication portion 71k is formed through the inside of the rotary valve 71 to form a hole. In such a first modified example, the same function and effect as in the first embodiment can be obtained.

Modification 2
FIG. 11 shows a second modification of the rotary valve of the first embodiment.

  The rotary valve 71 of the first embodiment has a structure in which the inlet 71f of the escape passage 71e and the two outlets 71g and 71h communicate with each other through one communication portion 71k (see FIG. 9), but the rotary valve shown in FIG. The second modification of 71 includes a communicating portion 71k-1 that communicates the inlet 71f and the first outlet 71g of the escape passage 71e, a communicating portion 71k-2 that communicates the inlet 71f and the second outlet 71h, Are provided separately. In addition, the communication part 71k-1 and the communication part 71k-2 are the structures which join on the way. In other words, the communication part 71k-1 and the communication part 71k-2 have a structure that branches off in the middle. In such a second modified example, the same effects as those in the first embodiment can be obtained.

(Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIGS.

  In the compressor 1 of the first embodiment, the rotary valve 71 is a plate-like rotary valve 71 that is in sliding contact with the valve plate 9. However, in the compressor 1 of the second embodiment, the rotary valve 71 </ b> A is the cylinder block 2. A central rotary valve 71A is slidable in the central through-hole 14, and the other structure is the same as that of the first embodiment.

  More specifically, as shown in FIGS. 12 and 13, a cylindrical portion 83 protrudes from the peripheral portion of the central through-hole 14 on the rear end surface of the cylinder block 2, and this cylindrical portion is the center of the valve plate 9. It protrudes into the suction chamber 7 formed in the rear head 6 through the through-hole 9c. Thus, the central through-hole 14 of the cylinder block 2 communicates with the suction chamber 7. The valve plate 9 is not provided with a suction hole, and is provided with a suction hole 11j in a partition wall 85 that divides the central through hole 14 of the cylinder block 2 and the cylinder bore Bj. A cylindrical rotary valve 71A is slidably rotated at the central through-hole 14 of the cylinder block 2, and the rotary valve 71A is connected to the drive shaft 10 and rotates integrally with the drive shaft 10. ing.

  Similarly to the first embodiment, the rotary valve 71A has a suction passage 71c that sequentially connects the suction hole 11j of the cylinder bore Bj during the suction stroke and the suction chamber 7 as the rotary valve 71A rotates. Is provided. The rotary valve 71A is provided with an escape passage 71e as in the first embodiment. The escape passage 71e is configured as a groove recessed in the surface of the rotary valve 71A, and communicates the inlet 71f, the first outlet 71g and the second outlet 71h, and the inlet 71f and the outlets 71g and 71h. 71k. The inlet 71f and the outlets 71g and 71h are provided on a rotation track overlapping the suction hole 11j, and sequentially communicate with the suction hole 11j when the rotary valve 71A rotates. The communication part 71k is provided at a position off the rotational track.

FIGS. 13 to 17 show the initial stage of the stroke of the cylinder bore B ₁ in the order of passage of time, and show how the escape passage 71e communicates with the cylinder bores B ₁ , B ₄ , B ₅ . In the state shown in FIG. 13, the piston P ₁ of the cylinder bore B ₁ is at the top dead center position, and the piston P ₄ of the cylinder bore B _{4 at} the 180 ° rotationally symmetric position is at the bottom dead center position. The cylinder bores B ₂ and B ₃ between the cylinder bore B ₁ at the bottom and the cylinder bore B ₄ at the bottom dead center are in the compression stroke, and the cylinder bore B ₄ at the bottom dead center and the cylinder bore at the top dead center The cylinder bores B ₅ and B ₆ between B ₁ are in the intake stroke.

Against the cylinder bore _{B 1} of the suction stroke initial stage, in the period (14 to 16) to release path inlet 71f is communicated with, first, as shown in FIG. 14, the first outlet 71g is the cylinder bore B ₁ of 180 ° after communicating with the cylinder bore B3 of the rotational direction one short of the opposite cylinder bore _{B 4,} shown in Figure 16, the second outlet 71h is the cylinder bore _{B 1} 180 ° opposite to the cylinder bore _{B 4} It comes to communicate with. Here, when the first outlet 71g is a period for communicating with the cylinder bore _{B 3} and A period (FIG. 14), the period during which the second outlet 71h communicates with the cylinder bore _{B 4} and C periods (Fig. 16), A period As shown in FIG. 15, the first outlet 71 g communicates with the suction hole 11 ₃ of the cylinder bore B ₃ , as shown in FIG. 15, between the (FIG. 14) and the C period (FIG. 16). outlet 71h there is a period B which communicates with the suction hole 11 ₄ of the cylinder bore _{B 4.}

  With the configuration as described above, the same effect as in the first embodiment can be obtained.

Modification 1
FIG. 19 shows a first modification of the rotary valve of the second embodiment.

  This first modified example is different from the one in which the communication portion 71k of the escape passage 71e is formed in a groove shape on the outer peripheral surface of the rotary valve 71A as in the rotary valve 71A of the second embodiment (FIGS. 13 and 18). The communication portion 71k is formed through the inside of the rotary valve 71A as a hole. In such a first modification, the same function and effect as in the second embodiment can be obtained.

Modification 2
FIG. 20 shows a second modification of the rotary valve of the second embodiment.

  This second modification is different from the structure (FIGS. 13 and 18) in which the inlet 71f of the escape passage 71e and the two outlets 71g and 71h communicate with each other through one communication portion 71k as in the rotary valve 71A of the second embodiment. A communicating portion 71k-1 that communicates the inlet 71f and the first outlet 71g of the escape passage 71e and a communicating portion 71k-2 that communicates the inlet 71f and the second outlet 71h are provided in a branched manner. Yes. In addition, the communication part 71k-1 and the communication part 71k-2 merge on the way. In such a second modified example, the operational effect can be obtained as in the second embodiment.

  Note that the present invention is not limited to the above-described embodiment.

  For example, in the above-described embodiment, the structure of the cylinder bore having six cylinders has been described as an example, but the present invention can also be applied to a structure in which an even number of four or more cylinder bores are provided at equal intervals in the circumferential direction. The present invention can be implemented in various other modes within the scope of the technical idea of the present invention.

FIG. 1 is a sectional view of a compressor according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view taken along the line ZZ in FIG. 1 and shows the positional relationship between the suction passage and the escape passage as the rotary valve rotates and the suction holes. FIG. 3 is a cross-sectional view taken along the line ZZ in FIG. 1 and shows the positional relationship between the suction passage and the escape passage accompanying the rotation of the rotary valve and the suction holes. FIG. 4 is a cross-sectional view taken along the line ZZ in FIG. 1 and shows the positional relationship between the suction passage and the escape passage along with the rotation of the rotary valve and the suction holes. FIG. 5 is a cross-sectional view taken along the line ZZ in FIG. 1 and shows a positional relationship between the suction passage and the escape passage accompanying the rotation of the rotary valve and the suction holes. FIG. 6 is a cross-sectional view taken along the line ZZ in FIG. 1 and shows the positional relationship between the suction passage and the escape passage along with the rotation of the rotary valve and the suction holes. FIG. 7 is a diagram in which the pressure curves in the cylinder bore B ₁ , cylinder bore B ₃ , and cylinder bore B ₄ are superimposed. In the figure, the solid line indicates the pressure curve in the cylinder bore B ₁ , and the alternate long and short dash line indicates the cylinder bore B. a line indicating the pressure curve in the _3, the two-dot chain line is a line indicating the pressure curve in the cylinder bore B _4. FIG. 8 is an enlarged view of the initial stage of the suction stroke of the cylinder bore B ₁ in FIG. FIG. 9 is a front view of the rotary valve of the compressor according to the first embodiment. FIG. 10 is a front view showing a first modification of the rotary valve of the compressor according to the first embodiment. FIG. 11 is a front view showing a second modification of the rotary valve of the compressor according to the first embodiment. FIG. 12 is a sectional view of a compressor according to a second embodiment of the present invention. FIG. 13 is a cross-sectional view taken along the line ZZ in FIG. 12 and shows the positional relationship between the suction passage and the escape passage along with the rotation of the rotary valve and the suction holes. FIG. 14 is a cross-sectional view taken along the line ZZ in FIG. 12 and shows the positional relationship between the suction passage and the escape passage accompanying the rotation of the rotary valve and the suction holes. FIG. 15 is a cross-sectional view taken along the line ZZ in FIG. 12 and shows the positional relationship between the suction passage and the escape passage and the suction holes as the rotary valve rotates. FIG. 16 is a cross-sectional view taken along the line ZZ in FIG. 1 and shows the positional relationship between the suction passage and the escape passage accompanying the rotation of the rotary valve and the suction holes. FIG. 17 is a cross-sectional view taken along the line ZZ in FIG. 1 and shows the positional relationship between the suction passage and the escape passage and the suction holes as the rotary valve rotates. FIG. 18 is a developed view of the outer peripheral surface of the rotary valve of the compressor according to the second embodiment. FIG. 19 is a cross-sectional view showing a first modification of the rotary valve of the compressor of the second embodiment. FIG. 20 is a cross-sectional view showing a second modification of the rotary valve of the compressor according to the second embodiment.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Compressor 7 ... Suction chamber 8 ... Discharge chamber 9 ... Valve plate (partition wall)
10 ... Drive shaft 11j (11 ₁ , 11 ₂ , 11 ₃ , 11 ₄ , 11 ₅ , 11 ₆ ) ... Suction hole 12j (12 ₁ , 12 ₂ , 12 ₃ , 12 ₄ , 12 ₅ , 12 ₆ ) ... Discharge hole 71 ... rotary valve 71c ... intake passage 71e ... relief passage 71f ... release passage inlet 71 g ... escape first outlet 71h ... relief second outlet 71k ... release path communicating section 83 ... partition wall Pj of passage of the passage _{(P 1} , P ₂ , P ₃ , P ₄ , P ₅ , P ₆ ) ... Piston Bj (B ₁ , B ₂ , B ₃ , B ₄ , B ₅ , B ₆ ) ... Cylinder bore

Claims (2)

An even number of four or more cylinder bores (Bj) provided at equal intervals in the circumferential direction around the drive shaft (10), and the cylinder bores (Bj) and a partition wall, and a suction hole formed in the partition wall A suction chamber (7) that communicates with the cylinder bore (Bj) through (11j), a compartment defined by the cylinder bore (Bj) and the partition wall, and communicates with the cylinder bore (Bj) through a discharge hole (12j) formed in the partition wall. A discharge chamber (8) and a piston (Pj) reciprocally disposed in each cylinder bore (Bj), and in each cylinder bore (Bj) in conjunction with the rotation of the drive shaft (10). As the pistons (Pj) sequentially reciprocate, a suction stroke and a discharge stroke are alternately performed in each cylinder bore (Bj), and in the suction stroke, the suction hole (11 ) Through the suction chamber (7) to the cylinder bore (Bj), and in the discharge stroke, the fluid is compressed in the cylinder bore (Bj), and the compressed fluid passes through the discharge hole (12j) to the cylinder bore (12j). A compressor (1) discharged from Bj) into the discharge chamber (8),
A rotary valve (71) that is rotatably slidably arranged so as to block the suction hole (11j) with respect to the partition wall and is coupled to the drive shaft (10) so as to rotate synchronously with the drive shaft (10). )
The rotary valve (71) has a suction passage (71c) that opens the suction hole (11j) of the cylinder bore (Bj) in the suction stroke and communicates the cylinder bore (Bj) and the suction chamber (7). At the same time, a release passageway (71e) through which the high-pressure residual fluid remaining without being discharged in the discharge stroke is released from the cylinder bore (Bj) in the initial stage of the suction stroke to another cylinder bore (Bj) having a pressure lower than that of the cylinder bore (Bj). Have
The escape passage (71e) includes an inlet (71f), a first outlet (71g) and a second outlet (71h) provided on a rotation track overlapping the suction hole (11j), and the suction hole (11j). And a communication portion (71k) that communicates with the inlet and the outlet off the rotating orbit overlapping with each other,
In a period in which the inlet (71f) of the escape passage (71e) communicates with the cylinder bore (Bj) in the initial stage of the suction stroke,
A: The first outlet (71g) communicates with the cylinder bore (Bj) one rotation direction before the cylinder bore (Bj) opposite to the cylinder bore (Bj) by 180 °,
C: Next, the compressor is characterized in that the second outlet (71h) communicates with a cylinder bore (Bj) on the opposite side of the cylinder bore (Bj) by 180 °. The compressor according to claim 1,
The compressor, wherein the A period and the C period partially overlap, and the A period and the C period are continuous without interruption.

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