CN203783895U - Scroll compressor - Google Patents

Abstract

The utility model provides a scroll compressor for effectively reducing the pressure of a refrigerant in an over-compression chamber so as to prevent the property and reliability from lowering because of over-compression. The scroll compressor is characterized in that a scroll compressor body (100) is provided with a discharging decompression flowing way (25) on a tooth root part (1g) of the inner side of a plate-shaped scroll tooth (1b) the range of a winding starting angle theta s of which is less than or equal to theta which is less than or equal to the sum of the theta s and twice of pi, the discharging decompression flowing way (25) is used for releasing a compressed over-compression refrigerant to a discharging hole (1d) and is independent from the discharging hole (1d), and a ball float valve (23) for opening and closing the discharging decompression flowing way (25) is stored on a bedplate part (1a) of a fixed scroll piece (1) as being pushed and pressed by a spring from the back.

Description

Scroll compressor

Technical field

The utility model relates to the scroll compressor using in freezing/air-conditioning purposes.

Background technique

In scroll compressor, be formed with scroll wrap interior to chamber and two of export-oriented chambers pressing chamber of fixed scroll, be accompanied by the rotation of bent axle, swing scroll and carry out revolution motion, thus, each pressing chamber narrows to central part from peripheral part, meanwhile, fluid is compressed and mobile.And then, following scroll compressor is disclosed: in pressing chamber, in the position of compression pilot process, in the mode of the platen portion that connects fixed scroll, pressure-reduction outlet is set, to the refrigeration agent excessively being boosted in pressing chamber is expelled to outside pressing chamber.

As such scroll compressor, proposition has the scroll compressor that possesses following structure: " except being positioned at the exhaust port of main body of central part of fixed scroll, when the coiling of involute being started to angle while being made as λ 1, it is another the second row outlet that the teeth groove portion in vortex body (rap) outside of the scope of λ 1 < λ≤λ 1+ π is provided with diameter and substantially approaches space width at winding angle λ, be provided with end face and the roughly plate valve of the coplanar for example seat surface with taper of alveolar surface in the time closing valve in this second row outlet " (for example, with reference to patent documentation 1).

Patent documentation 1: Japanese kokai publication sho 59-119080 communique (the second-3 page, Fig. 5 etc.)

The vortex structure of the scroll compressor shown in above-mentioned patent documentation 1 is to swing that the scroll wrap of scroll and the scroll wrap of fixed scroll stagger in position that the intermeshing mode in position of 180 ° combines and the structure of the identical form of the volume of two pressing chambers forming.And then, be formed as second row outlet to be arranged on the structure of the export-oriented face side of the scroll wrap of this fixed scroll.

Herein, finish near the compressor of vortex structure end at the coiling that there is the interior sidewall surface that the coiling of the scroll wrap of fixed scroll is finished to end and extend to the scroll wrap that swings scroll, in the time that above-mentioned second row outlet is arranged on to the export-oriented face side of scroll wrap of fixed scroll, be formed as following structure: the scroll wrap of the fixed scroll easily rising with pressure in pressing chamber interior to compared with the pressing chamber of face, the pressing chamber of export-oriented face easily reduces pressure.Therefore, worry cannot be given full play to the effect that is provided with above-mentioned second row outlet.

Model utility content

The utility model is complete in order to solve above-mentioned problem, its object is the scroll compressor that provides following: finish near the compressor of vortex structure end at the coiling that has the interior sidewall surface that the coiling of the scroll wrap of fixed scroll is finished to end and extend to the scroll wrap that swings scroll, can more effectively reduce pressure to the refrigeration agent in the pressing chamber of overcompression, can prevent that the performance causing due to overcompression from reducing and reliability reduces.

The utility model relates to a kind of scroll compressor, and above-mentioned scroll compressor has: swing scroll, above-mentioned swing scroll possesses platen portion and is formed at the tabular scroll wrap of this platen portion; Fixed scroll, above-mentioned fixed scroll possesses platen portion and is formed at the tabular scroll wrap of this platen portion; and seal container, above-mentioned swing scroll and above-mentioned fixed scroll are incorporated in above-mentioned seal container under the tabular scroll wrap with mutual staggers in position the state that the intermeshing mode in position of 180 ° combines, under the state that above-mentioned swing scroll and above-mentioned fixed scroll are combined, the coiling that the inwall side that the coiling of the tabular scroll wrap of above-mentioned fixed scroll finishes end extends to the tabular scroll wrap of above-mentioned swing scroll finishes near end, by make above-mentioned swing scroll not from then carry out revolution motion, refrigeration agent after compressed in the pressing chamber being formed by the tabular scroll wrap of two scroll is discharged to the back side of above-mentioned fixed scroll from being arranged at the exhaust port of central part of above-mentioned fixed scroll, it is the discharge space in above-mentioned seal container, above-mentioned scroll compressor is characterised in that, in above-mentioned fixed scroll, with above-mentioned exhaust port independently, when the coiling of the tabular scroll wrap of above-mentioned fixed scroll being started to the tooth root portion of inner side of the tabular scroll wrap of the scope in θ s≤θ≤θ s+2 π while being made as θ s, angle, be provided with the discharge decompression stream that refrigeration agent is discharged to above-mentioned exhaust port, in the inside of the platen portion of above-mentioned fixed scroll, to be accommodated with the float-controlled valve that above-mentioned discharge decompression stream is opened and closed from the mode of the back side pushing of above-mentioned fixed scroll by spring.

And the related scroll compressor of the utility model is characterised in that, above-mentioned discharge decompression stream is formed as the rounded shape of flowing path section.

And the related scroll compressor of the utility model is characterised in that, above-mentioned float-controlled valve is formed as, and is closing under the state of above-mentioned discharge decompression stream, and the bottom surface of the face on the top of above-mentioned float-controlled valve and the tabular scroll wrap of above-mentioned fixed scroll is coplanar.

And the related scroll compressor of the utility model is characterised in that, above-mentioned float-controlled valve is configured to drum with the level, and the inside of receiving the platen portion of the above-mentioned fixed scroll of above-mentioned float-controlled valve is also processed to step shape.

And the related scroll compressor of the utility model is characterised in that, at the back side of above-mentioned fixed scroll, is provided with the expulsion valve of the opening portion that stops up above-mentioned exhaust port.

For the related scroll compressor of the utility model, for being expelled to, the refrigeration agent after compressed discharges space, with the exhaust port that is formed on fixed scroll independently, when the coiling of the tabular scroll wrap of fixed scroll being started to the tooth root portion of inner side of the tabular scroll wrap of the fixed scroll of the scope in θ s≤θ≤θ s+2 π while being made as θ s, angle, be provided with the discharge decompression stream that the overcompression refrigeration agent after compressed is discharged to exhaust port, bear the float-controlled valve of the effect that this discharge decompression stream is opened and closed to be incorporated in the platen portion of fixed scroll from the mode of its back side pushing by spring.

Thus, the scroll compressor related according to the utility model, can more effectively reduce pressure to overcompression refrigeration agent, and the performance that can significantly suppress to cause because of overcompression reduces and reliability reduces.

Brief description of the drawings

Fig. 1 is the general profile chart that the unitary construction of the related scroll compressor of mode of execution 1 of the present utility model is roughly shown.

Fig. 2 is the sectional view that the state after the compression mechanical part of scroll compressor related mode of execution 1 of the present utility model is amplified is shown.

Fig. 3 be for and associated with respect to the position of the associated and pressing chamber between the relative position of fixed scroll and pressure-reduction outlet and float-controlled valve of the swing scroll of the related scroll compressor of mode of execution of the present utility model 1, the complete state of suction of the interior pressing chamber to face of the scroll wrap of fixed scroll is made as to 0 °, illustrates until compress the figure of complete process with the interval of 90 °.

Fig. 4 is the sectional view that the state after the compression mechanical part of scroll compressor related mode of execution 2 of the present utility model is amplified is shown.

Fig. 5 is for associated with respect to the relative position of fixed scroll with the swing scroll of existing general scroll compressor, and the complete state of suction of the interior pressing chamber to face of the scroll wrap of fixed scroll is made as to 0 °, illustrates until compress the figure of complete process with the interval of 90 °.

Fig. 6 is the plotted curve that the relation of the volume-variation of the pressing chamber of existing general scroll compressor and pressure is compared and illustrated according to the state of head pressure.

Label declaration

1: fixed scroll; 1A: fixed scroll; 1a: platen portion; 1b: tabular scroll wrap; 1bA: tabular scroll wrap; 1c: crosshead steering channel; 1d: exhaust port; 1e: pressure-reduction outlet; 1eA: pressure-reduction outlet; 1f: float-controlled valve accommodating groove; 1g: tooth root portion; 2: swing scroll; 2A: swing scroll; 2a: platen portion; 2b: tabular scroll wrap; 2bA: tabular scroll wrap; 2c: oscillation bearing; 2d: thrust face; 2e: crosshead steering channel; 2f: boss part; 2g: boss part space; 2h: boss part outer space; 2i: platen peripheral part space; 2j: bleeder hole; 2k: open lower side portion; 3: flexible frame; 3a: thrust-bearing; 3c: main bearing; 3d: upper chimeric barrel surface; 3e: lower chimeric barrel surface; 3h: auxiliary spindle holds; 3m: spring; 3n: intercommunicating pore; 3p: intermediate pressure is adjusted valve accommodation space; 3s: intercommunicating pore; 3t: intermediate pressure is adjusted valve; 3u: upside opening portion; 3x: face; 3y: valve guard; 4: main shaft; 4b: swing axial region; 4c: main shaft part; 4d: countershaft portion; 4f: oil pipe; 4g: high pressure oil oil supply hole; 6: subframe; 6a: supplementary bearing; 7: motor stator; 8: motor rotor; 9: crosshead mechanism; 9a: swing side switch; 9b: crosshead mechanism annulus; 9c: fixing side switch; 10: seal container; 10d: discharge space; 10e: refrigerator oil; 15: guiding frame; 15a: upper chimeric barrel surface; 15b: lower chimeric barrel surface; 15f: frame space; 16a: upper Sealing; 16b: lower seal; 17a: counterweight; 17b: counterweight; 20: pressing chamber; 20A: pressing chamber; 20a: pressing chamber; 20aA: pressing chamber; 20b: pressing chamber; 20bA: pressing chamber; 21: bolt; 22: spring; 23: float-controlled valve; 25: discharge decompression stream; 26: plate; 30: safety check; 32: bolt; 33: reduction valve; 34: valve guard; 35: expulsion valve; 42: suction pipe; 43: discharge tube; 100: scroll compressor; 100A: scroll compressor; 200: scroll compressor.

Embodiment

Below, based on accompanying drawing, mode of execution of the present utility model is described.In addition, including Fig. 1, in following accompanying drawing, there is the magnitude relationship situation different from actual conditions of each component parts.And including Fig. 1, in following accompanying drawing, the part of mark same numeral is identical or suitable part, this is identical in the full text of specification.In addition, the form of the constituting component showing in specification full text is only illustrating, and is not limited to these records.

［ about existing scroll compressor ］

First, based on Fig. 5 and Fig. 6, existing general scroll compressor (hereinafter referred to as " compressor 100A ") is described.Fig. 5 is for associated with respect to the relative position of fixed scroll with the swing scroll of compressor 100A, and the complete state of suction of the interior pressing chamber to face of the scroll wrap of fixed scroll is made as to 0 °, illustrates until compress the figure of complete process with the interval of 90 °.Fig. 6 is the plotted curve that the relation of the volume-variation of the pressing chamber of compressor 100A and pressure is compared and illustrated according to the state of head pressure.In addition, about the parts relevant with compressor 100A, identify at label end mark " A ".And, for Fig. 6, in the mode of execution of the present utility model 1,2 of following explanation, use too.

The coiling that the inwall side that the coiling that compressor 100A is formed as the tabular scroll wrap 1bA that makes fixed scroll 1A finishes end extends to the tabular scroll wrap 2bA that swings scroll 2A finishes near the structure of end near.In compressor 100A, be formed with tabular scroll wrap 1bA interior to chamber and two of export-oriented chambers pressing chamber 20A(pressing chamber 20aA, pressing chamber 20bA of fixed scroll 1A), swing scroll 2A is accompanied by the rotation of bent axle (omitting diagram) and carries out revolution motion, thus, each pressing chamber narrows to central part from peripheral part, meanwhile, fluid is compressed and mobile.

In this compressor 100A, the interior of the tabular scroll wrap 1bA of fixed scroll 1A do not form to the pressing chamber 20aA of face and the pressing chamber 20bA of export-oriented face simultaneously, aspect starting, produces the phase difference of approximately 180 ° in compression.Therefore, the interior pressing chamber 20aA to face of the tabular scroll wrap 1bA of fixed scroll 1A is with respect to the pressing chamber 20bA of export-oriented face and long 180 ° between compressing area, and both sides' compression ratio there are differences.

The interior volume to the pressing chamber 20aA of face and the pressing chamber 20bA of export-oriented face of the tabular scroll wrap 1bA of the fixed scroll 1A of the moment of formation pressing chamber 20A is made as respectively to Vsi, Vso, and will in each pressing chamber, compress complete and be made as respectively Vdi, Vdo by the volume before being communicated with exhaust port, the pressure of each pressing chamber is now made as to Pdi, Pdo, suction pressure is made as to Ps, changeable (polytrope) index is made as to n, and following formula is set up.

$P_{\mathrm{di}}={\left(\frac{V_{\mathrm{di}}}{V_{\mathrm{si}}}\right)}^n{P}_s,P_{\mathrm{do}}={\left(\frac{V_{\mathrm{do}}}{V_{\mathrm{so}}}\right)}^n{P}_s,\frac{V_{\mathrm{di}}}{V_{\mathrm{si}}}>\frac{V_{\mathrm{do}}}{V_{\mathrm{so}}}$

Fig. 6 represents to have the volume-variation of pressing chamber 20A and the relation of pressure in the compressor 100A of this mechanism.The head pressure determining in refrigerating plant side and become the pressure in the seal container of compressor 100A is made as to Pd, according to the state of head pressure Pd, the pressure oscillation difference of the inside of pressing chamber 20A.

In Fig. 6 (a), the running in the situation that pressure P di, Pdo when head pressure Pd is more complete than the compression of two pressing chamber 20A is large is shown.,, in the operating condition shown in Fig. 6 (a), in the time that compression is complete, two pressing chamber 20A all become the insufficient compression state of the head pressure Pd not reaching in seal container.Therefore, the refrigeration agent in seal container temporarily flows into pressing chamber 20A due to this pressure difference by exhaust port, produces large recompression loss.

In Fig. 6 (b), illustrate below the pressure P di of head pressure Pd in the time that the compression of pressing chamber 20aA is complete and more than pressure P do when complete in the compression of pressing chamber 20bA operating condition.; in the operating condition shown in Fig. 6 (b); in the time that compression is complete; pressure P di when the compression of pressing chamber 20aA is complete becomes overcompression state more than the head pressure Pd reaching in seal container, but the pressure P do of the compression of pressing chamber 20bA when complete becomes the insufficient compression state of the head pressure Pd not reaching in seal container.Therefore,, in the time of pressing chamber 20A and exhaust port connection, due to this pressure difference, in the time that refrigeration agent is discharged in seal container, produce overcompression loss.

In Fig. 6 (c), the operating condition in the situation that pressure P di, Pdo when head pressure Pd is more complete than the compression of two pressing chamber 20A is little is shown.,, in the operating condition shown in Fig. 6 (c), in the time that compression is complete, two pressing chamber 20A all become the overcompression state of the head pressure Pd having reached in seal container.Therefore,, due to this pressure difference, in the time that refrigeration agent is discharged in seal container, produce large overcompression loss.

And, in compressor 100A, in the time starting under the state in liquid refrigerant is trapped in seal container and in pressing chamber 20A, understand the stress more than intensity that produces abnormal pressure rise, produces scroll wrap (tabular scroll wrap 1bA, tabular scroll wrap 2bA), thus, sometimes become the reason of compressor fault.In order to prevent above-mentioned situation, consider to adopt following countermeasure: in pressing chamber, in the mode of the platen portion of perforation fixed scroll, pressure-reduction outlet is set in the position of compression pilot process, the refrigeration agent excessively being boosted in pressing chamber is discharged outward towards pressing chamber.

But, because the diameter of pressure-reduction outlet need to, below the transverse tooth thickness of scroll wrap, therefore exist the situation that cannot obtain sufficient effect of easing stress for pressing chamber internal volume.Therefore, as recorded in above-mentioned patent documentation 1, consider to adopt following structure: pressure-reduction outlet is not only set, in order to obtain further effect of easing stress, in the time that beginning angle that the vortex of fixed scroll is reeled is made as λ a, the tooth root face that is the export-oriented face of the scroll wrap of the fixed scroll of the scope of λ a < λ≤λ a+ π at winding angle λ arranges second row outlet.But, even if in the scroll compressor of recording at patent documentation 1, also there is problem as above.

［ mode of execution 1 ］

Fig. 1 is the general profile chart that the unitary construction of the related scroll compressor of mode of execution 1 of the present utility model (hereinafter referred to as " compressor 100 ") is diagrammatically shown.Fig. 2 is the sectional view that the state after the compression mechanical part of compressor 100 is amplified is shown.Fig. 3 is for associated with respect to the associated and pressing chamber of the relative position of fixed scroll and the position of pressure-reduction outlet and float-controlled valve with the swing scroll of compressor 100, and the complete state of suction of the interior pressing chamber to face of the scroll wrap of fixed scroll is made as to 0 °, illustrates until compress the figure of complete process with the interval of 90 °.Structure and the action of Fig. 1～Fig. 3 to compressor 100 describes.

Compressor 100 is for example applied to the freezing cycle device of refrigerator, freezer, vending machine, air conditioner, refrigerating plant, hot water supply device etc.That is, compressor 100 has following functions: suck the fluids such as the refrigeration agent that circulates in freeze cycle, compress and become the state of high temperature, high pressure and discharge.

The structure > of < compressor 100

Compressor 100 has: fixed scroll 1, swing scroll 2, flexible frame 3, main shaft 4, and subframe 6, motor stator 7, motor rotor 8, crosshead mechanism 9, guiding frame 15, and receive the seal container 10 of above-mentioned each parts.

In addition, seal container 10 be connected with by refrigeration agent be drawn into seal container 10 inside suction pipe 42 and the refrigeration agent after compressed is discharged to the outside discharge tube 43 of seal container 10.

(fixed scroll 1)

Fixed scroll 1 has the 1a of platen portion and tabular scroll wrap 1b, and the peripheral part of the 1a of platen portion is fastened onto guiding frame 15 by bolt (not shown).Fixed scroll 1 is configured in the superjacent air space of seal container 10 as shown in Figure 1.Tabular scroll wrap 1b is formed on a side's of the 1a of platen portion face (downside in figure).And, at a side's of the peripheral part of fixed scroll 1 face (downside in figure), be formed with two a pair of crosshead steering channel 1c in general arrangement mode point-blank.Two a pair of fixing side switch 9c of crosshead mechanism 9 engage with this crosshead steering channel 1c to come and go mobile mode freely.

And, illustrating as amplified in Fig. 2, be provided with and compression overcompression refrigeration agent midway can be released into a pair of pressure-reduction outlet 1e in seal container 10 at the 1a of platen portion of fixed scroll 1.The rounded shape of flowing path section of this pressure-reduction outlet 1e.

And, in the planar surface portion of the side opposition side forming with pressing chamber 20 of fixed scroll 1, be provided with a pair of reduction valve 33 to cover the mode of pressure-reduction outlet 1e.Reduction valve 33 is fixed in the planar surface portion of fixed scroll 1 together with valve guard 34 by bolt 32.

And, be provided with the exhaust port 1d that the refrigeration agent after compressed is expelled to the space (discharging space 10d) of the inner and upper of seal container 10 at the central part of the 1a of platen portion of fixed scroll 1.

And, when the coiling of the vortex of fixed scroll 1 being started to angle while being made as θ s, the 1g of tooth root portion of the inner side of the tabular scroll wrap 1b of the scope at winding angle θ in θ s≤θ≤θ s+2 π, is provided with the overcompression refrigeration agent after compressed to exhaust port 1d discharge decompression release, that form in the mode of the rounded shape of flowing path section stream 25.And then the float-controlled valve 23 of bearing the effect that the stream of discharge decompression stream 25 is opened and closed is incorporated in the inside (the float-controlled valve accommodating groove 1f shown in figure) of the 1a of platen portion in the mode of being pressed from its back side by spring 22.Float-controlled valve accommodating groove 1f is processed to form as two-stage step shape by perforate, has hole large-diameter portion and hole minor diameter part.

In addition, float-controlled valve 23 is formed as drum with the level (being two-stage step drum in the drawings), is provided with O shape ring 24 in the cylindrical part periphery of path, and the pressure of discharging in decompression stream 25 and seal container 10 is sealed.And then, in order to prevent that engaging from having float-controlled valve 23 and the spring 22 of O shape ring 24 to come off from the 1a of platen portion, to cover the mode of the float-controlled valve accommodating groove 1f that is arranged at the 1a of platen portion, is fixed with plate 26 in the upper plane of fixed scroll 1 by bolt 21.

And be formed as: in the time that the hole large-diameter portion that is formed as the large-diameter portion of float-controlled valve 23 of two-stage step drum and the interface of minor diameter part and same perforate and is processed into the float-controlled valve accommodating groove 1f of two-stage step shape contacts with the interface of hole minor diameter part, close under the state of discharging decompression stream 25, the top plane of the minor diameter part of float-controlled valve 23 and the 1g of tooth root portion are substantially coplanar.Further be formed as: under the state after compressor 100 assemblings, between the swing top plane of tabular scroll wrap 2b of scroll 2 and the top plane of the minor diameter part of float-controlled valve 23, produce small gap.

(swinging scroll 2)

Swing the tabular scroll wrap 2b that scroll 2 has the 2a of platen portion and be same shape with the tabular scroll wrap 1b essence of fixed scroll 1, and be configured to make tabular scroll wrap 1b and tabular scroll wrap 2b engagement.Swing the downside that scroll 2 is disposed at as shown in Figure 1 the superjacent air space of seal container 10 and is configured in fixed scroll 1.Tabular scroll wrap 2b is formed at a side's of the 2a of platen portion face (upside in figure).And then, by making tabular scroll wrap 1b and tabular scroll wrap 2b engage to form pressing chamber 20.Be accompanied by the spinning movement that swings scroll 2, the volume of pressing chamber 20 relatively changes.

And, at the central part 2a of platen portion and face tabular scroll wrap 2b opposition side (downside in figure), be formed with the boss part 2f of hollow cylindrical.At the inner side surface of this boss part 2f, i.e. boss part space 2g, be formed with oscillation bearing 2c.

And, the 2a of platen portion with the peripheral part of face of face same side that is formed with boss part 2f, be formed with the thrust face 2d that can slide with the thrust-bearing 3a crimping of flexible frame 3.

And, swinging a side the face (downside in figure) of peripheral part of the 2a of platen portion of scroll 2, be formed with the crosshead steering channel 1c of fixed scroll 1 and there is a pair of crosshead steering channel 2e of two of phase differences of 90 degree roughly in general arrangement mode point-blank.Two a pair of swing side switch 9a of crosshead mechanism 9 engage with this crosshead steering channel 2e in the mode coming and going sliding freely.

And, being formed with bleeder hole 2j at the 2a of platen portion that swings scroll 2, this bleeder hole 2j is the thin hole of diameter that the face (face of downside in Fig. 1) of the face of fixed scroll 1 side (face of upside in Fig. 1) and flexible frame 3 sides is communicated with.And then its circle track at the opening portion by the face of flexible frame side, when the set positions of the 2k of open lower side portion becomes in running conventionally of this bleeder hole 2j is housed in the inside of the thrust-bearing 3a of flexible frame 3 all the time.

(flexible frame 3, guiding frame 15)

Flexible frame 3 have by swing scroll 2 support the function for sliding.Flexible frame 3 is configured in and swings forming surface opposition side scroll 2 and tabular scroll wrap 2b (downside in figure).Flexible frame 3 is supported by guiding frame 15.

Guiding frame 15 is fixed in the inside of seal container 10, has via flexible frame 3 fixed scroll 1 and swings the function that supports of scroll 2.It is rotation function freely by the upper support of main shaft 4 that guiding frame 15 also has via flexible frame 3.

Be formed with face 3x in the outside of the thrust-bearing 3a of flexible frame 3.The annulus 9b of crosshead mechanism of crosshead mechanism 9 comes and goes sliding movement on this face 3x.

And, at the central part of flexible frame 3, be formed with the main bearing 3c and the auxiliary spindle that on radial direction, the main shaft 4 being rotarilyd actuate by motor are supported and hold 3h.

And, at flexible frame 3, be formed with the position of the 2k of the open lower side portion face-off that is formed at the bleeder hole 2j that swings scroll 2 the intercommunicating pore 3s that is communicated to frame space 15f from thrust-bearing 3a.In addition, the thrust-bearing opening portion of intercommunicating pore 3s, i.e. upper shed portion (opening portion of upside in Fig. 1) are called to upside opening portion 3u.

And, be formed with the intercommunicating pore 3n that is communicated with platen peripheral part space 2i and frame space 15f at the face 3x of flexible frame 3.

And, be provided with at flexible frame 3: the intermediate pressure of adjusting the pressure of boss part outer space 2h is adjusted valve 3t; Valve guard 3y; And adjust valve accommodation space 3p for receiving the intermediate pressure of spring (intermediate pressure adjustment spring) 3m.And then the spring 3m that adjusts intermediate pressure is compressed compared with natural length, is then incorporated in intermediate pressure and adjusts valve accommodation space 3p.

And, as shown in Figure 1, being formed with upper chimeric barrel surface 15a in fixed scroll 1 side (upside in Fig. 1) of the inner side surface of guiding frame 15, upper chimeric barrel surface 15a engages with the upper chimeric barrel surface 3d of the outer circumferential face that is formed at flexible frame 3.

On the other hand, be formed with lower chimeric barrel surface 15b at the motor side (downside in Fig. 1) of the inner side surface of guiding frame 15, lower chimeric barrel surface 15b engages with the lower chimeric barrel surface 3e of the outer circumferential face that is formed at flexible frame 3.

The upper and lower of the frame space 15f being formed by the inner side surface of guiding frame 15 and the outer side surface of flexible frame 3 divided by upper Sealing 16a, the lower seal 16b of ring-type.For exemplifying, but also sealing groove can be formed to the outer circumferential face of flexible frame 3 with the situation that is formed with the seal groove of the ring-type of Sealing 16a, lower seal 16b in two places storages at the inner peripheral surface of guiding frame 15 herein.

In addition, up and down by swing the 2a of platen portion of scroll 2 and the outer circumferential side of the thrust-bearing 3a that flexible frame 3 surrounds space, platen peripheral part space 2i is formed as sucking the low-voltage space of refrigeration agent atmosphere (suction pressure).

(main shaft 4)

Main shaft 4 is rotarilyd actuate by motor, and this main shaft 4 makes to swing scroll 2 and rotates.Be formed with the swing axial region 4b engaging in rotation mode freely with the oscillation bearing 2c that swings scroll 2 in swing scroll 2 sides (upside in the figure) end of main shaft 4.

And, be formed with main bearing 3c and the auxiliary spindle of flexible frame 3 and hold the main shaft part 4c that 3h engages in rotation mode freely at the downside that swings axial region 4b.

And, be formed with the 4d of countershaft portion engaging in rotation mode freely with the supplementary bearing 6a of subframe 6 in the other end of main shaft 4.Between this 4d of countershaft portion and main shaft part 4c, shrink fit has motor rotor 8.

In addition, be pressed into oil pipe 4f in the lower end surface of main shaft 4, the refrigerator oil 10e of the bottom that lodges in seal container 10 can have been drunk up.

In addition, rotate by main shaft 4, the high pressure oil oil supply hole 4g of the inside of the refrigerator oil 10e being drunk up by oil pipe 4f by being formed at main shaft 4 is supplied to each slide part.

(other structure)

Subframe 6 is fixed in the below, inside of seal container 10, has and together with guiding frame 15, main shaft 4 is supported as rotation function freely., main shaft 4 up by guiding frame 15, below be supported to respectively rotation freely by subframe 6.

Motor stator 7 separates specified gap and is configured in motor rotor 8 outer circumferential sides, by starting energising, motor rotor 8 is rotated to driving.And the outer circumferential face of motor stator 7 is fixedly attached to seal container 10 by shrink fit etc.

Motor rotor 8 is fixed in the main shaft part 4c of main shaft 4, and motor stator 7 is switched on and is driven in rotation by starting, thereby main shaft 4 is rotated.In addition, at the upper surface of motor rotor 8, counterweight 17a is installed, at the lower surface of motor rotor 8, counterweight 17b is installed.

Motor stator 7 and motor rotor 8 form motor.

The counterweight 17a and the counterweight 17b that are installed on motor rotor 8 rotate together with motor rotor 8, have the function that realizes mass balance (static state and transient equiliblium) for this rotation.In addition, counterweight 17a and counterweight 17b are installed in motor rotor 8 by for example riveting etc.

Crosshead mechanism 9 is disposed in the thrust face side that swings scroll 2, and performance stops the spinning motion of swing scroll 2 and make to swing scroll 2 function that can carry out oscillating motion.This crosshead mechanism 9 has: the annulus 9b of crosshead mechanism that is formed as ring-type; Be arranged at two a pair of fixing side switch 9c of the upper surface of the annulus 9b of crosshead mechanism; And be arranged at two a pair of swing side switch 9a of the lower surface of the annulus 9b of crosshead mechanism.Fixing side switch 9c and swing side switch 9a arrange so that mutually orthogonal mode is outstanding.Fixing side switch 9c engages with crosshead steering channel 1c to come and go slip mode freely.Swinging side switch 9a engages with crosshead steering channel 2e to come and go slip mode freely.

Seal container 10 forms the external frame of compressor 100, and inner and upper is formed as discharging space 10d, and inner below is formed as low-voltage space.The bottom of seal container 10 is formed for storing the oily reservoir of refrigerator oil 10e.And, be connected with suction pipe 42 for sucking refrigeration agent and the discharge tube 43 for discharging refrigerant at seal container 10.In addition, suction pipe 42 and discharge tube 43 are all connected in a part for the side of seal container 10.And, be provided with the safety check 30 of the adverse current for preventing refrigeration agent at the entrance of suction pipe 42.

The action > of < compressor 100

Action to compressor 100 describes.

In the time of the quiet rum of compressor 100, the discharge space 10d of seal container 10 is formed as the high pressure of discharging refrigerant atmosphere.Therefore, the refrigerator oil 10e of the bottom of seal container 10 at oil pipe 4f and connect vertically in the high pressure oil oil supply hole 4g that main shaft 4 arranges in Fig. 1 towards above flow.The refrigerator oil 10e flowing in high pressure oil oil supply hole 4g and be directed to the high pressure of boss part space 2g is depressurized at oscillation bearing 2c.This refrigerator oil 10e becomes intermediate pressure higher than suction pressure and below head pressure, and flows to boss part outer space 2h.

On the other hand, as another paths, in high pressure oil oil supply hole 4g, the refrigerator oil 10e of mobile high pressure is directed to the high pressure side end face of main bearing 3c from being arranged at the cross-drilled hole (diagram is omitted) of main shaft 4.This refrigerator oil 10e is depressurized and becomes intermediate pressure at this main bearing 3c, and flows to equally boss part outer space 2h.

For the refrigerator oil 10e that becomes intermediate pressure of boss part outer space 2h, owing to being dissolved in the foaming of refrigeration agent of refrigerator oil 10e, conventionally become the two-phase flow of gaseous refrigerant and refrigerator oil, and when adjust valve accommodation space 3p by intermediate pressure, overcome the power that applied by spring 3m and intermediate pressure is adjusted to valve 3t boost and flow to frame space 15f.Then, refrigerator oil 10e is the inner side that intercommunicating pore 3n is discharged to the annulus 9b of crosshead mechanism through the stream having passed through after intermediate pressure adjustment valve 3t.

On the other hand, as another paths, refrigerator oil 10e is being supplied to the inner side that is discharged to the annulus 9b of crosshead mechanism after the slide part swinging between the thrust face 2d of scroll 2 and the thrust-bearing 3a of flexible frame 3.

And then, be released into platen peripheral part space 2i from the refrigerator oil 10e that is discharged from being supplied to the slip surface of the annulus 9b of crosshead mechanism of crosshead mechanism 9 and key slip surface here.

As discussed above, in compressor 100, the intermediate pressure Pm1 of boss part outer space 2h is exposed the regulation that area determines pressure alpha by the intermediate pressure of roughly adjusting valve 3t according to the elastic force of spring 3m and intermediate pressure is controlled in the mode of Pm1=Ps+ α (Ps be suck atmosphere pressure be low pressure).

On the other hand, the 2k of open lower side portion of bleeder hole 2j that is arranged at the 2a of platen portion that swings scroll 2 is the opening portion of upside in upside opening portion 3u(Fig. 1 with the thrust-bearing opening portion of the intercommunicating pore 3s that is arranged at flexible frame 3) be communicated with all the time or connection off and on.Therefore, high than the compression that comes from by fixed scroll 1 and swing the pressing chamber 20 that scroll 2 forms suction pressure midway and be directed to frame space 15f via swinging the bleeder hole 2j of scroll 2 and the intercommunicating pore 3s of flexible frame 3 for the refrigeration agent of the intermediate pressure below head pressure.

But, though be directed, but because frame space 15f is by upper Sealing 16a and the airtight enclosed space of lower seal 16b, therefore in the time of quiet rum, be formed as echoing mutually with the pressure oscillation of pressing chamber 20 and pressing chamber 20 and frame space 15f twocouese have pettiness flow, so-called breathing state.

As discussed above, in compressor 100, the multiplying power β of the regulation that the intermediate pressure Pm2 of frame space 15f roughly determines according to the position of the pressing chamber 20 by being communicated with is controlled in the mode of Pm2=Ps × β (Ps is that suction atmosphere pressure is low pressure).

At flexible frame 3, as power down, effect has making a concerted effort of the power being caused by the intermediate pressure Pm1 of boss part outer space 2h and the pushing force that swinging scroll 2 via next the coming from of thrust-bearing 3a transmission.On the other hand, at flexible frame 3, as power upward, effect has the power that caused by the intermediate pressure Pm2 of frame space 15f and because acting on making a concerted effort of power that the high pressure of the part that is exposed to high pressure atmosphere of lower end surface causes.And then, in compressor 100, set for: in the time of quiet rum, the power upward that acts on flexible frame 3 is greater than power down.

Therefore, the upper chimeric barrel surface 15a guiding of the directed framework 15 of upper chimeric barrel surface 3d of flexible frame 3, the lower chimeric barrel surface 15b guiding of the directed framework 15 of lower chimeric barrel surface 3e, be that flexible frame 3 can slide axially with respect to guiding frame 15, can float towards fixed scroll side (top in Fig. 1).And then the swing scroll 2 being pushed by flexible frame 3 via thrust-bearing 3a is floated towards top too, result, the tooth top that swings scroll 2 contacts with tooth top and slides with each tooth root of fixed scroll 1 with tooth root.

Based on Fig. 3, the action of compressor 100 is described in more detail.

In the vortex structure of compressor 100, swing the tabular scroll wrap 2b of scroll 2 and the tabular scroll wrap 1b of fixed scroll 1 and combine in the intermeshing mode in position of 180 ° of staggering in position, the volume of two pressing chambers is identical.And then the coiling that compressor 100 uses the inwall side that the coiling of tabular scroll wrap 1b is finished to end to extend to tabular scroll wrap 2b finishes near the fixed scroll 1 end., as shown in Figure 3, the coiling of the tabular scroll wrap 1b of fixed scroll 1 finishes coiling that end (end of most peripheral side) extends to tabular scroll wrap 2b finishes near of end (end of most peripheral side).

Therefore,, in compressor 100, the interior of tabular scroll wrap 1b do not form to the pressing chamber 20a of face and the pressing chamber 20b of export-oriented face simultaneously, aspect starting, produces the phase difference of approximately 180 ° in compression.Therefore,, in the time that the angle of rotation of the moment of the interior pressing chamber 20a to face of the tabular scroll wrap 1b of formation is made as to 0 °, in this moment, also do not form pressing chamber (Fig. 3 (a)) at the export-oriented face of tabular scroll wrap 1b.Become the moment of 180 ° in angle of rotation, form pressing chamber 20b(Fig. 3 (c) of the export-oriented face of the tabular scroll wrap 1b of fixed scroll 1).

Then,, in compressor 100, both sides' pressing chamber (pressing chamber 20a, pressing chamber 20b) carries out the compression of refrigeration agent on one side towards central mobile on one side.And then, become the moment of 630 ° in angle of rotation, tabular scroll wrap 2b interior to face and export-oriented face respectively from the export-oriented face of fixed scroll 1 and interiorly leave to face, thus, the compression of both sides' pressing chamber is complete, and the discharge space 10d from exhaust port 1d to seal container 10 discharges (Fig. 3 (h)).

In the overcompression running of the existing compressor 100A shown in Fig. 5 (b) and Fig. 5 (c), passed through the moment of approximately 360 ° in angle of rotation, the pressure-reduction outlet 1eA of fixed scroll 1A is communicated with each pressing chamber (pressing chamber 20aA, pressing chamber 20bA).Therefore,, when in the time that the pressure of this each pressing chamber of moment reaches head pressure Pd, reduction valve is opened, and in seal container, is depressurized.But, because the diameter of pressure-reduction outlet 1eA need to, for swinging below the thickness of tabular scroll wrap 2bA of scroll 2A, therefore exist the situation that cannot obtain sufficient effect of easing stress.

On the other hand, in compressor 100, in the time that angle of rotation reaches approximately 540 ° (Fig. 3 (g)), the interior pressing chamber 20a to face of tabular scroll wrap 1b arrives the top planar surface portion of float-controlled valve 23.Now, if the pressure in the seal container 10 that the pressure of pressing chamber 20a is faced higher than the plane of the large-diameter portion side of float-controlled valve 23 and the power sum that produced by spring 22, float-controlled valve 23 moves towards top.Therefore, discharging decompression stream 25 opens.Thus, at the export-oriented face of tabular scroll wrap 2b from interior the leaving to face of fixed scroll 1 and before refrigeration agent is discharged from, overcompression refrigeration agent can be discharged to (solid arrow shown in Fig. 2 and Fig. 3 (g)) by the discharge stream 25 that reduce pressure to exhaust port 1d.

Now, because the pressure of the pressing chamber 20b of the export-oriented face of the tabular scroll wrap 1b of pressure ratio of the interior pressing chamber 20a to face of tabular scroll wrap 1b is high, therefore can obtain larger effect of easing stress, can prevent that the performance that causes due to overcompression from reducing and because the reliability that is accompanied by the compressor that the abnormal ascending of pressure of liquid refrigerant compression etc. causes reduces.

In running under the insufficient compression state shown in Fig. 6 (a), pressing chamber 20a when approximately 630 ° of angle of rotation and the pressure of pressing chamber 20b do not reach the head pressure Pd in seal container 10.Therefore, reduction valve 33 keeps cutting out and can not open, and float-controlled valve 23 does not also rise.Now, float-controlled valve 23 does not rise, and the 1g of tooth root portion of the top plane of its minor diameter part and fixed scroll 1 continues coplanar, therefore, until the side face of tabular scroll wrap 2b is left from the side face of tabular scroll wrap 1b, can proceed compression.

As above, for compressor 100, with exhaust port 1d dividually, when the coiling of tabular scroll wrap 1b being started to the 1g of tooth root portion of tabular scroll wrap 1b inner side of the scope in θ s≤θ≤θ s+2 π while being made as θ s, angle, be provided with the discharge decompression stream 25 that the overcompression refrigeration agent after compressed is discharged to exhaust port 1d, bear the float-controlled valve 23 of the effect that this discharge decompression stream 25 is opened and closed to be incorporated in the 1a of platen portion by spring 22 from the mode of its back side pushing, therefore, can more effectively reduce pressure to overcompression refrigeration agent, the performance that can significantly suppress to cause due to overcompression reduces and reliability reduces.

［ mode of execution 2 ］

Fig. 4 is the sectional view that the state after the compression mechanical part of scroll compressor related mode of execution 2 of the present utility model (hereinafter referred to as " compressor 200 ") is amplified is shown.Based on Fig. 4, compressor 200 is described.In addition, the structure of the basic structure of compressor 200 compressor 100 related with mode of execution 1 is identical.And, in mode of execution 2, by with the difference of mode of execution 1 centered by describe, to the part mark same numeral identical with mode of execution 1 and description thereof is omitted.

The same freezing cycle device that is for example applied to refrigerator, freezer, vending machine, air conditioner, refrigerating plant, hot water supply device etc. of compressor 100 that compressor 200 is related with mode of execution 1.That is, compressor 200 has following functions: suck the fluids such as the refrigeration agent that circulates in freeze cycle, compress and become high temperature, high pressure conditions and discharge.

The structure > of < compressor 200

Compressor 200 is except the structure of the related compressor 100 of mode of execution 1, also be provided with expulsion valve 35 in the mode of opening portion that covers exhaust port 1d fixed scroll 1 and planes pressing chamber 20 opposition sides, this expulsion valve 35 is fixed by bolt 32 together with valve guard 34.

The action > of < compressor 200

When tabular scroll wrap 2b interior that swings scroll 2 to face and export-oriented face respectively from the export-oriented face of the tabular scroll wrap 1b of fixed scroll 1 and interiorly leave to face, when the compression of refrigeration agent is complete, by the pressure of the refrigeration agent in pressing chamber 20, expulsion valve 35 is opened upward, and refrigeration agent is discharged to the discharge space 10d of seal container 10.

Action when overcompression shown in Fig. 6 (c) the running compressor 100 related with mode of execution 1 is identical, also can obtain same effect in compressor 200.But, in the related compressor 100 of mode of execution 1, recompression loss under insufficient compression operating condition in the pressing chamber 20b of the export-oriented face side of the tabular scroll wrap 1b of the fixed scroll 1 shown in Fig. 6 (a) and Fig. 6 (b) cannot reduce, and correspondingly likely causes performance to reduce.

In such insufficient compression running, in compressor 200, when tabular scroll wrap 2b interior that swings scroll 2 to face and export-oriented face respectively from the export-oriented face of the tabular scroll wrap 1b of fixed scroll 1 and interior while leaving to face, the temporary transient adverse current of refrigeration agent that is discharged from the head pressure Pd in the exhaust port 1d that valve 35 stops up is to pressing chamber 20 and produce recompression loss, but the volume of the refrigeration agent of this head pressure Pd is because the effect of expulsion valve 35 is limited.Therefore,, according to compressor 200, this loss can be suppressed to inferior limit.

Thus, in compressor 200, except the effect that the related compressor 100 of mode of execution 1 plays, owing to can reducing the overcompression overcompression loss in when running, therefore can significantly suppress further reliability and reduce.

Claims (8)

1. a scroll compressor,

Described scroll compressor has:

Swing scroll, described swing scroll possesses platen portion and is formed at the tabular scroll wrap of this platen portion;

Fixed scroll, described fixed scroll possesses platen portion and is formed at the tabular scroll wrap of this platen portion; And

Seal container, described swing scroll and described fixed scroll are incorporated in described seal container under the tabular scroll wrap with mutual staggers in position the state that the intermeshing mode in position of 180 ° combines,

Under the state that described swing scroll and described fixed scroll are combined, the coiling that the inwall side that the coiling of the tabular scroll wrap of described fixed scroll finishes end extends to the tabular scroll wrap of described swing scroll finishes near end,

By make described swing scroll not from then carry out revolution motion, refrigeration agent after compressed in the pressing chamber being formed by the tabular scroll wrap of two scroll is discharged to the back side of described fixed scroll, i.e. discharge space in described seal container from being arranged at the exhaust port of central part of described fixed scroll

Described scroll compressor is characterised in that,

In described fixed scroll, with described exhaust port independently, when the coiling of the tabular scroll wrap of described fixed scroll being started to the tooth root portion of inner side of the tabular scroll wrap of the scope in θ s≤θ≤θ s+2 π while being made as θ s, angle, be provided with the discharge decompression stream that refrigeration agent is discharged to described exhaust port

In the inside of the platen portion of described fixed scroll, to be accommodated with the float-controlled valve that described discharge decompression stream is opened and closed from the mode of the back side pushing of described fixed scroll by spring.

2. scroll compressor according to claim 1, is characterized in that,

Described discharge decompression stream is formed as the rounded shape of flowing path section.

3. scroll compressor according to claim 1 and 2, is characterized in that,

Described float-controlled valve is formed as, and is closing under the state of described discharge decompression stream, and the bottom surface of the face on the top of described float-controlled valve and the tabular scroll wrap of described fixed scroll is coplanar.

4. scroll compressor according to claim 1 and 2, is characterized in that,

Described float-controlled valve is configured to drum with the level,

The inside of receiving the platen portion of the described fixed scroll of described float-controlled valve is also processed to step shape.

5. scroll compressor according to claim 3, is characterized in that,

Described float-controlled valve is configured to drum with the level,

The inside of receiving the platen portion of the described fixed scroll of described float-controlled valve is also processed to step shape.

6. according to the scroll compressor described in any one in claim 1,2,5, it is characterized in that,

At the back side of described fixed scroll, be provided with the expulsion valve of the opening portion that stops up described exhaust port.

7. scroll compressor according to claim 3, is characterized in that,

At the back side of described fixed scroll, be provided with the expulsion valve of the opening portion that stops up described exhaust port.

8. scroll compressor according to claim 4, is characterized in that,

At the back side of described fixed scroll, be provided with the expulsion valve of the opening portion that stops up described exhaust port.