CN1534191A - Piston-type compressor - Google Patents

Abstract

A gasket is provided between a cylinder block and a valve plate. By providing a through hole at a position near the center of the gasket, bending moment acting on the cylinder block is reduced, and hence deformation of the cylinder block is restrained. As a result, reciprocating motion of a piston and rotational motion of a rotary valve are performed smoothly.

Description

Piston compressor

Technical field

The present invention relates to a kind of piston compressor that is used for vehicle air conditioning, more particularly, relate to a kind of technology that suppresses the cylinder block distortion.

Background technique

For example, Japanese publication JP8-14160 has described a kind of packing ring 101, as shown in figure 13.This packing ring 101 is used for the piston compressor of vehicle air conditioning.

Packing ring 101 has 103, one groups of patchholes 105 of one group of through hole and a center hole 106, and wherein through hole 103 is corresponding with the edge of opening of the cylinder-bore 102 of holding piston basically, and through bolt 104 penetrates in the patchhole 105, and live axle inserts in the center hole 106.As a kind of piston compressor that is equipped with this packing ring 101, piston compressor shown in the local enlarged cross-sectional view of Figure 14 is many known, front case parts 108 are connected in the front-end face (left side as shown in the figure) of cylinder block 107, rear case parts 110 are connected in the ear end face (the right as shown in the figure) of cylinder block 107 by valve plate 109, and front case parts 108, rear case parts 110 and valve plate 109 are fastening mutually by through bolt 104.In this piston compressor, packing ring 101 is folded between cylinder block 107 and the valve plate 109.As shown in figure 15, cylinder block 107 has cylinder-bore 102 and receiving cavity 111, and wherein this receiving cavity 111 is used for holding the rotary valve that sucks refrigerant gas.

In the described piston compressor of above-mentioned publication, when through bolt 104 was tightened, cylinder block 107 was born bending moment and is out of shape.Especially, as shown in figure 14, under the fastened situation of through bolt 104, on the joint surface between cylinder block 107 and the front case parts 108, act on the front-end face of cylinder block 107 from the specific pressure f1 of front case parts 108.And, on the joint surface between the sealing surface of cylinder block 107 and packing ring 101, act on the ear end face of cylinder block 107 from the specific pressure f2 of valve plate 109.

Get a bit arbitrarily as point of action P1 on the front-end face of cylinder block 107, wherein specific pressure f1 acts on this P1; Get a bit arbitrarily as point of action P2 on the ear end face of cylinder block 107, wherein specific pressure f1 acts on this P2; Straight line H tie point P1 and P2, bending moment M is around center P 3 effects of straight line H so.Because the effect of bending moment M, the directed force F m that makes progress in the footpath of packing ring 101 is applied on point of action P1 and the P2, thus cylinder block will be out of shape, shown in the dot and dash line of Figure 15.Thereby, with worrying be that the level and smooth to-and-fro motion of piston will be hindered owing to distortion.

And, as shown in figure 15, when the receiving cavity 111 that is used for rotary valve is formed on cylinder block 107, will make receiving cavity 111 easy deformation because the rigidity of cylinder block 107 is low.Therefore, the level and smooth rotation of rotary valve will be suppressed.

Summary of the invention

An object of the present invention is to provide a kind of piston compressor, in this piston compressor, thereby act on the distortion that bending moment on the cylinder block will reduce to suppress cylinder block, thereby the motion of piston and rotary valve will carry out improving the endurance of piston compressor smoothly.

In order to reach aforementioned and other purposes, purpose according to the present invention provides a kind of piston compressor, and this piston compressor has a cylinder block, front case parts, and rear case parts, one runs through bolt, one group of piston, a live axle and a packing ring.Cylinder block has one group of cylinder-bore.Cylinder block has both ends of the surface, and cylinder-bore is in this both ends of the surface upper shed.The front case parts are fixed on one of cylinder block both ends of the surface, and the rear case parts are fixed on the other end of cylinder block, and valve plate is interposed between rear case parts and the cylinder block.The fastening cylinder block of through bolt, rear case parts and front case parts.Each piston is contained in the cylinder-bore and to-and-fro motion therein, and the drive shaft piston is also supported rotatably by cylinder block, the to-and-fro motion compression of piston and discharge refrigerant gas.Packing ring is arranged between cylinder block and the valve plate.Packing ring has a center hole and one group of bore hole, the arrangement of aliging with a cylinder-bore of each bore hole.One first through hole is formed on the bending moment that is used for reducing to be created in cylinder block on the packing ring when through bolt is tightened.This first through hole is arranged between a pair of adjacent bore hole and is arranged in an imaginary annulus.The center of this imagination annulus is corresponding with the bore hole center, and the radius of this imagination annulus is first radius.This first radius value is to the distance the bore hole center from the packing ring center.

By the description of embodiment, make others of the present invention and beneficial effect will seem very clear below in conjunction with accompanying drawing to principle of the present invention.

Description of drawings

Reach following detailed description of the preferred embodiment in conjunction with the accompanying drawings, can thoroughly understand the present invention and purpose and beneficial effect, accompanying drawing is as follows:

Fig. 1 is the cross-sectional view of the piston compressor of first embodiment of the invention;

Fig. 2 is a partial cross section view shown in Figure 1;

Fig. 3 is arranged on the front elevation of the packing ring in the compressor shown in Figure 1;

Fig. 4 is the front elevation that is used for explaining first embodiment's conventional gaskets;

Fig. 5 is a plotted curve, expression must have seal action hermetic unit circumferential length and in packing ring apart from the relation between the distance at packing ring center;

Fig. 6 is a plotted curve, the expression need not have seal action hermetic unit circumferential length and in packing ring apart from the relation between the distance at packing ring center;

Fig. 7 is a plotted curve, and expression is created in total change amount of the bending moment in the cylinder block;

Fig. 8 is the cross-sectional view of the piston compressor among second embodiment;

Fig. 9 is arranged on the front elevation of the packing ring in the compressor shown in Figure 8;

Figure 10 is the front elevation that is used to explain second embodiment's conventional gaskets;

Figure 11 is the front elevation of the packing ring in the alternate embodiment;

Figure 12 is the front elevation of the packing ring in another alternate embodiment;

Figure 13 is the front elevation of packing ring of the prior art;

Figure 14 is the partial cross section view of piston compressor of the prior art; With

Figure 15 is the partial cross section view of piston compressor of the prior art.

Embodiment

Referring to Fig. 1 to 7, will describe the first embodiment of the present invention in detail below.

As shown in Figure 1, in the variable displacement piston compressor in the first embodiment of the present invention, front case parts 3 are connected to by packing ring 2 on the front-end face of cylinder block 1, and the crank chamber 4 that is used as control chamber is limited in the inside of these front case parts 3.Rear case parts 6 are connected on the ear end face of cylinder block 1 by valve plate 5, exhaust chamber 7 and induction chamber 8 are limited in the inside of these rear case parts 6, packing ring 9 is folded between cylinder block 1 and the valve plate 5, outlet valve forms plate 10 and is interposed between valve plate 5 and the rear case parts 6, and wherein this outlet valve forms plate 10 and outlet valve and baffle plate formation plate 11 whole formation that are used for forming baffle plate.Cylinder block 1, front case parts 3 and rear case parts 6 are fastening by through bolt 12 (Fig. 1 is not shown).

In the axis hole of the core that is formed at cylinder block 1 and front case parts 3, live axle 13 supports by radial bearing 14a and 14b with being rotated.One shaft sealer 15 is arranged on the fore-end of live axle 13.In crank chamber 4, otic placode 16 is fixed on the live axle 13 with live axle 13 rotations, is set up with a certain state as the swash plate 17 of cam disk, and wherein in this state, live axle 13 inserts in the through hole that is formed in the swash plate 17.One articulated mounting 18 is interposed between otic placode 16 and the swash plate 17.Supporting effect by articulated mounting 18 and live axle 13 is articulated and connected between swash plate 17 and otic placode 16, thereby swash plate 17 can rotatablely move with otic placode 16 and live axle 13, and when swash plate 17 during along the endwisely slipping of live axle 13, swash plate 17 tilts with respect to live axle 13.

One group of cylinder-bore 19 along the circumferential direction is arranged on cylinder block 1, and each cylinder-bore 19 is held the piston 20 that can move back and forth.Pressing chamber 21 is limited between each piston 20 and the valve plate 5, and the volume of this pressing chamber 21 changes according to the to-and-fro motion of piston 20.Each piston 20 engages with the outer peripheral portion branch of swash plate 17 by a pair of sliding wedge 22.Thereby, when live axle 13 rotatablely moves, driving swash plate 17 by otic placode 16 and articulated mounting 18 and be rotated motion, rotatablely moving of swash plate 17 is transformed into the to-and-fro motion of piston by sliding wedge 22.Otic placode 16, swash plate 17, articulated mounting 18 and sliding wedge 22 have constituted a crank mechanism, and this crank mechanism is transformed into rotatablely moving of live axle 13 and is used for the compression movement of in pressing chamber 21 compression refrigeration gas.

Rotary valve receiving cavity 23 is formed in the cylinder block 1, and in rotary valve receiving cavity 23, rotary valve 24 is connected on the live axle 13 rotatablely moving synchronously with live axle 13 by coupling 25.The air intake passage 26 that always keeps communicating with induction chamber 8 is formed in the rotary valve 24, and the outlet 27 of air intake passage 26 is an opening on the external peripheral surface of rotary valve 24.Through hole 28 is formed in the cylinder block 1.Each through hole and each pressing chamber 21 are corresponding and the outlet 27 of rotary valve 24 is communicated with corresponding pressing chamber 21.

When the live axle 13 of drive power source compressor, swash plate 17 is rotated motion by otic placode 16 and articulated mounting 18, to such an extent as to piston 20 moves back and forth in cylinder-bore 19 by sliding wedge 22.In the suction stroke of piston 20, the outlet 27 of rotary valve 24 links to each other with each through hole 28, to such an extent as to the refrigerant gas in the induction chamber 8 is inhaled in each pressing chamber 21 by air intake passage 26.Further, when each piston 20 carried out compression stroke and exhaust stroke, respective through hole 28 was closed by the outer peripheral surface of rotary valve 21, thereby the refrigerant gas in the pressing chamber 21 is pushed outlet valve open and is discharged in the exhaust chamber 7.

Next will describe main points of the present invention in detail.At first, in the present embodiment, act on the cylinder block 1 active force as shown in Figure 2.Under the situation that through bolt 12 is tightened, on the joint surface between cylinder block 1 and the front case parts 3, act on the front end surface of cylinder block 1 from the specific pressure f1 of front case parts 3.And, on the joint surface between the sealing surfaces of cylinder block 1 and packing ring 9, act on the rear end surface of cylinder block 1 from the specific pressure f2 of packing ring 9.

Get a bit arbitrarily as point of action P1 on the front-end face of cylinder block 1, wherein specific pressure f1 acts on this P1; Get a bit arbitrarily as point of action P2 on the ear end face of cylinder block 1, wherein specific pressure f2 acts on this P2, straight line H tie point P1 and P2, and bending moment M is around center P 3 effects of straight line H so.The beeline that makes progress in packing ring 9 footpaths between point of action P1 and the P2 is represented with D1, represent with D2 in through bolt 12 beeline on axially between point of action P1 and the P2, because bending moment M is created in radial force on two point of action P1 and the P2 when representing with Fm, bending moment M calculates by following equation and obtains so, and equation is as follows:

Fm＝f2·(D1/D2) (1)

M＝Fm·D2＝f2·D1 (2)

Can find directed force F m and bending moment M with increasing from these two equatioies from packing ring 9 and the increase that acts on the specific pressure f2 on the ear end face of cylinder block 1, or along with point of action P2 and packing ring 9 are adjoining and increase.

Packing ring 9 in the present embodiment as shown in Figure 3.Packing ring 9 is made by ferrous metals plate and the rigid base that the elasitic layer (as rubber) with sealability constitutes, and wherein elasitic layer is coated on two end surfaces of base.And, packing ring 9 have one group basically with suitable bore hole 29 (having 6 in the present embodiment) and the one group of bolt hole 30 (having 6 in the present embodiment) of the edge of opening of cylinder-bore 19, through bolt 12 is inserted in this bolt hole 30.One through hole is formed in a certain annulus, wherein the radius of this annulus is the distance R b from packing ring 9 centers to each bore hole 29 center, center hole 31 in this through hole and the conventional gaskets (as shown in Figure 3, this through hole is formed in the annulus of dot and dash line formation) corresponding with first through hole 32, through hole 32 communicates mutually.It is that center radius is that the annulus and of Rb is that center radius is between the annulus of Rc with packing ring 9 centers with packing ring 9 centers that second through hole 33 is formed on one.Can find out obviously that from Fig. 2 in the scope that is provided with first through hole 32 and second through hole 33, specific pressure f2 does not act on the cylinder block 1, to such an extent as to do not produce bending moment.Because bigger in the position bending moment that is adjacent to packing ring 9 centers, so through hole 32 and 33 can reduce this bending moment.

Referring to Fig. 4-Fig. 7, will explain the meaning of radius R c and the method for definite radius R c below.Fig. 4 represents traditional packing ring 34, and this packing ring 34 has bore hole 29, bolt hole 30 and center hole 31.In Fig. 4, the solid line dash area is the hermetic unit that must have sealing through hole 29, bolt hole 30 and compressor internal action.That is to say that in packing ring 34, the scope except solid line dash area, through hole 29, bolt hole 30 and center hole 31 (the dotted line dash area among Fig. 4) expression must not have the part of washer sealing effect.Fig. 5 and Fig. 6 have represented respectively and must and not need to have the length (this annulus is that center radius is x with packing ring 34 center O) of the hermetic unit of seal action on a certain annulus circumference in the length that has the hermetic unit of seal action on a certain annulus circumference (this annulus is that center radius is x with packing ring 34 center O).Rg represents the radius of packing ring 34.At this, replenish and describe " length (this annulus is that center radius is x with packing ring 34 center O) that must on a certain annulus circumference, have the hermetic unit of seal action ".For example, the length (this annulus is that center radius is A with packing ring 34 center O) that has the hermetic unit of seal action on a certain annulus circumference is represented with La, the length that does not need to have the hermetic unit of seal action on the annulus circumference is represented with Lb, can find out clearly that from Fig. 4 the representation of La and Lb is as follows:

La＝L1+L3+L5+L7+L9+L11

Lb＝L2+L4+L6+L8+L10+L12

As shown in Figure 5 and Figure 6, the formula (3) of the hermetic unit area S of packing ring 34 is as follows:

$S={\∫}_0^{\mathrm{Rg}}f\left(x\right)\mathrm{dx}+{\∫}_0^{\mathrm{Rg}}g\left(x\right)\mathrm{dx}+{\∫}_{\mathrm{RB}}^{\mathrm{Rg}}h\left(x\right)\mathrm{dx}------\left(3\right)$

In the superincumbent formula (3), function f (x) is the function of curve shown in Figure 5, and function g (x) is the function of curve shown in Figure 6 in 0≤x≤Rb scope, and function h (x) is the function of curve shown in Figure 6 in Rb≤x≤Rg scope.

Further, when tightening through bolt 12, the total pressure that is applied on the whole sealing surface of packing ring 34 represents that with F the specific pressure f2 on the unit area of sealing surface is expressed as follows:

f2＝F/S

Total pressure F is according to the shape of screwing force, cylinder block and the rear case parts of bolt and rigidity and decide, in the total pressure F in the present embodiment and the traditional compressor total pressure equate.

Then, suppose the through hole with minute widths Δ x is arranged on does not need to have seal action on circumferential section part (this circumference is that center radius is x with the center O).This moment, the area S (x) of hermetic unit was calculated by following two formula:

$S\left(x\right)=S-{\∫}_x^{x+\mathrm{\Δx}}g\left(x\right)\mathrm{dx}(0\≤x\≤\mathrm{Rb})-----\left(4\right)$

$S\left(x\right)=S-{\∫}_x^{x+\mathrm{\Δx}}h\left(x\right)\mathrm{dx}(\mathrm{Rb}\≤x\≤\mathrm{Rg})-----\left(5\right)$

When being provided with the through hole with minute widths Δ x, the increasing amount of specific pressure represents that with Δ f2 the formula of Δ f2 is as follows: Δ f2=F/S (x)-F/S, wherein this formula uses above-mentioned formula (4) and (5).

Therefore, when the increasing amount of bending moment was represented with Δ M1, Δ M1 calculated by following formula (6), and wherein this formula (6) uses above-mentioned formula (1) and above-mentioned Δ f2.

$\mathrm{\&Delta;<figure-callout\; id="1"\; label="M"\; filenames="A20041003526600121.png"\; state="\{\{state\}\}">M</figure-callout>}1={\&Integral;}_0^{\mathrm{Rg}}(\mathrm{\&Delta;<figure-callout\; id="2"\; label="f"\; filenames="A20041003526600121.png,A20041003526600161.png"\; state="\{\{state\}\}">f</figure-callout>}2\&CenterDot;x)\mathrm{dx}------\left(6\right)$

And owing to the decrease that through hole causes bending moment to reduce is represented with Δ M2, by using above-mentioned formula (2), the formula of Δ M2 is as follows:

ΔM1＝f2·x (7)

Therefore, when through hole is arranged on need be when circumferential section have the part (this circumference is that center radius is x with the center O) of seal action, total this variable of bending moment is represented with Δ M (=Δ M2-Δ M1), Δ M is shown in the curve of Fig. 7, and wherein this curve negotiating uses formula (6) and (7) to draw.Rc is defined as from center O to certain any distance, wherein at this some place, Δ M1=Δ M2 (≠ 0).In Fig. 7, Rc represents certain a bit, in the Δ M=0 of this some place (situation of getting rid of Δ M1=Δ M2=0).

Fig. 7 represents: if through hole is formed in a certain annulus, this annulus is that center radius is Rc with the center O, because owing to through hole causes decrease that bending moment reduces greater than the increasing amount that causes bending moment to increase owing to specific pressure, thereby total bending moment will reduce.

In this embodiment, being used for the inside and outside hermetic unit of hermetic compressor is formed on the excircle part of packing ring 9.Can find out obviously that from Fig. 2 bending moment is not created on the joint surface 35 between cylinder block 1 and the packing ring 9, but live axle 13 axially on joint surface between cylinder block 1 and front case parts 3.Therefore, packing ring 9 forms sealing surfaces and suits in the scope of joint surface 35, thereby reduces specific pressure Δ f2 as wide as possible.

By this embodiment, the bending moment that acts on the cylinder block 1 reduces, thereby has suppressed the distortion of cylinder block 1.Therefore, suppressed the distortion of cylinder-bore 19, thereby the to-and-fro motion of piston 20 will be level and smooth.And, suppressed to be used for to hold the distortion of the rotary valve receiving cavity 23 of rotary valve 24, thereby rotatablely moving of rotary valve 24 can be level and smooth.Further, increased the specific pressure of packing ring by reducing sealing surface, thereby improved the sealability of packing ring, even perhaps the screwing force of bolt is compared with respect to traditional compressor and reduced also can guarantee the sufficient sealability of packing ring.Therefore, can suppress the distortion of cylinder block 1 further, thereby improve the endurance of compressor by the screwing force that reduces bolt.

Then, referring to Fig. 8 to 10 various details second embodiment.In a second embodiment, difference with first embodiment shown in Fig. 1 to 7 has been described.Identical reference character is represented identical or like, and this description identical or like will be omitted at this.

Fig. 8 represents five cylinder compressors.In this compressor, rotary valve 24 and rotary valve receiving cavity 23 as the air suction structure of refrigerant gas, not the substitute is: Aspirating valves forms plate 36 and is folded between cylinder block 1 and the valve plate 5, and packing ring 37 is folded in Aspirating valves and forms between plate 36 and the cylinder block 1.In the suction stroke of each piston 20, corresponding Aspirating valves is opened, and refrigerant gas flows through and is formed on the corresponding suction port on the valve plate 5 and is inhaled in the pressing chamber 21.Further, when piston 20 carried out air-breathing and compression stroke, Aspirating valves cut out, suction port close and pressing chamber 21 in refrigerant gas push outlet valve open and be discharged in the exhaust chamber 7.

As shown in Figure 9, in the packing ring 37 in the present embodiment, a through hole 38 forms under a certain state, in this state, and center hole 31 (being arranged in the annulus shown in Fig. 9 dotted line), first through hole and second through hole communicate mutually.In the piston compressor in the present embodiment, compare with above-mentioned first embodiment, the quantity of piston is reduced to five.Figure 10 has represented to be used for the piston type compressed conventional gaskets of five cylinders 39.In Figure 10, dash area is the hermetic unit that must have sealing through hole 29, bolt hole 30 and compressor internal action.Can find out obviously that from Figure 10 in packing ring 39, the part between the adjacent through-holes 29 is the hermetic unit that need not have seal action.Thereby, owing to the packing ring 39 that has in the present embodiment, thereby, center hole, first through hole and second through hole can wholely form through hole 38 by being communicated mutually.Therefore, reduce bending moment, thereby suppressed the distortion of cylinder block 1.And by forming whole through hole 38 in such a manner, the model that need be used for making packing ring 37 is made easily, and will prolong the working life of this model, thereby has reduced manufacture cost like this.

For a person skilled in the art, the present invention can also have other embodiment in not breaking away from essence of the present invention or scope.Especially, be to be understood that the present invention can also have following form.

Shown in Figure 11 and 12, the center hole 31 and first through hole 32 can be separated from each other.

In these embodiments, owing to reduced the distortion that bending moment has then suppressed cylinder block, so the motion of piston and rotary valve will be level and smooth, thus improved the enduring quality of piston compressor.

Example of the present invention and embodiment are illustrative, rather than restrictive, and the present invention is not limited to the detailed description at this, the present invention and below claims institute restricted portion in can change.

Claims (10)

1, a kind of piston compressor, it comprises:

One cylinder block, this cylinder block have one group of cylinder-bore, and this cylinder block has two end faces, has cylinder-bore on this end face;

One front case parts, these front case parts are installed on the end face of cylinder block;

One rear case parts, these rear case parts are installed on the other end of cylinder block, and wherein valve plate is folded between these front case parts and the rear case parts;

One runs through bolt, and this through bolt is used for fastening cylinder block, rear case parts and front case parts;

One group of piston, each piston are contained in the cylinder-bore and move back and forth therein;

One live axle, this drive shaft piston is also supported rotatably by cylinder block, the to-and-fro motion compression of piston and discharge refrigerant gas; It is characterized in that:

One packing ring, it is arranged between cylinder block and the valve plate, and its middle washer has a center hole and one group of bore hole, and each bore hole aligns with one of cylinder-bore; First through hole is formed on the packing ring, thereby when through bolt is tightened, has reduced to be created in the bending moment in the cylinder block; First through hole is arranged between a pair of adjacent through hole and is positioned at an imaginary annulus, and the center of this imagination annulus is consistent with the bore hole center, and the radius of imaginary annulus is first radius, and this first radius is to the distance at the center of one of bore hole from the center of packing ring.

2, compressor according to claim 1 is characterized in that:

This imagination annulus is the first imaginary annulus, and the second imaginary annulus with second radius is considered to around the packing ring center, the big predetermined value of this second radius ratio, first radius; Second through hole is formed on the packing ring, thereby when through bolt is tightened, has reduced bending moment; Second through hole is arranged on certain part of packing ring, and this part is between the second imaginary annulus and the first imaginary annulus.

3, compressor according to claim 2 is characterized in that:

First through hole communicates with second through hole.

4, compressor according to claim 1 is characterized in that:

This imagination annulus is the first imaginary annulus, and the second imaginary annulus with second radius R c is considered to around the packing ring center, and the second radius R c is not equal to first radius; Second through hole is formed on the packing ring, thereby when through bolt is tightened, has reduced to be created in the bending moment in the cylinder block; Second through hole is arranged on certain part of packing ring, and this part is between the second imaginary annulus and the first imaginary annulus; With

When running through through hole and be tightened, for the pressure that is applied to owing to packing ring in the cylinder-bore, do not have at packing ring under the situation of first and second through holes, f represents pressure; Do not have at packing ring under the situation of first and second through holes, Δ f represents the increasing amount of pressure f, and this moment, one through hole was formed in the second imaginary annulus of packing ring; R represents that apart from any distance at packing ring center, the value of the second radius R c is so determined so: fRc equals the integral value of Δ fR in from the packing ring center to packing ring entire radius scope.

5, compressor according to claim 4 is characterized in that: do not have at packing ring under the situation of first and second through holes, fRc represents the decrease of bending moment, and this moment, one through hole was formed in the second imaginary annulus of packing ring; Integral value is represented the increasing amount of bending moment, this moment through hole be formed on second this moment through hole be formed in the second imaginary annulus of packing ring, packing ring does not have first and second through holes.

6, compressor according to claim 4 is characterized in that:

First through hole communicates with second through hole.

7, according to the described compressor of arbitrary claim in the claim 1 to 6, it is characterized in that:

First through hole communicates with center hole.

8, according to the described compressor of arbitrary claim in the claim 1 to 6, it is characterized in that:

Pressing chamber is limited in each cylinder-bore by corresponding piston, this compressor further comprises a suction pressure region, with rotary valve with the live axle rotation, wherein the internal pressure of this suction pressure region is a pressure of inspiration(Pi), wherein rotary valve has an introducing passage, when live axle rotated, this introducing passage was used for refrigerant gas is incorporated into pressing chamber from suction pressure region.

9, according to the described compressor of arbitrary claim in the claim 2 to 6, it is characterized in that:

Cylinder-bore is provided with at interval around the axle equal angles of cylinder block.

10, compressor according to claim 9 is characterized in that:

This first through hole is in one group of first through hole, and this second through hole is in one group of second through hole, and wherein this first through hole is provided with at interval around packing ring center equal angles, and one of each second through hole and first through hole form a pair of through hole.

Images