CN101990593A

CN101990593A - Rotary piston machine

Info

Publication number: CN101990593A
Application number: CN2009801064648A
Authority: CN
Inventors: 赫伯特·许特林
Original assignee: Individual
Current assignee: Individual
Priority date: 2008-02-26
Filing date: 2009-02-07
Publication date: 2011-03-23
Also published as: DE102008012374A1; WO2009106216A1; EP2255070A1; DE102008012374B4

Abstract

The invention relates to a rotary piston machine having a housing (12) in which at least one first piston (22) is disposed that can revolve about a rotary axis (30) fixed to the housing, performing reciprocating motions when revolving about the rotary axis (30) between an end position near the rotary axis and an end position away from the rotary axis (30), in order to periodically reduce and enlarge a working chamber (34) bounded by an end face (38) of the piston (22) facing the rotary axis (30), wherein the rotary axis (30) runs through the working chamber (34), wherein the piston (22) comprises a control element (70) running along a control curve (66) fixed to the housing as the piston (22) revolves about the rotary axis (30), in order to derive the reciprocating motions of the piston (22) from the revolving motion, and wherein the piston (22) is disposed in a receptacle of a piston cage (50) to which the piston is rotationally fixed relative to the rotary axis (30) and that revolves about the rotary axis (30) together with the piston (22). The piston (22) comprises, in addition to the control element (70), a support element (88) on the centrifugal force side relative to the rotary axis (30), the running surface (108) thereof rolling along the inner side of the piston cage (50) during the reciprocating motion of the piston (22), wherein the direction of motion of the support element (88) and the rotary axis (30) lie in a common plane.

Description

Rolling piston compressor

Technical field

The present invention relates to a kind of rolling piston compressor, has housing, at least one first piston is set in housing, it can center on the rotating shaft revolution fixing with housing, and it is implementing to-and-fro motion around rotating shaft when revolution between near the end position of rotating shaft and the end position away from rotating shaft, with so that the working room by piston towards the end face of rotating shaft limits periodically become big and diminish, wherein, rotating shaft is passed the working room and is extended, piston has the control travelling mechanism, edge and the fixing control cam operation of housing when it turns round around rotating shaft at piston, be used for deriving the to-and-fro motion of piston from rotation motion, and piston is arranged in the receiving means of piston retainer, and piston is connected with the piston retainer antitorquely for rotating shaft, and the piston retainer turns round around rotating shaft with piston.

Background technique

DE102006009197A1 discloses this rolling piston compressor.

Can be used as internal-combustion engine (explosive motor), pump or compressor according to rolling piston compressor of the present invention.Preferably be used as internal-combustion engine and be described in this manual according to rolling piston compressor of the present invention as internal-combustion engine.

With this rolling piston compressor as under the situation of internal-combustion engine, by the to-and-fro motion of at least one piston between two end positions coordinate the entering of fuel-air mixture, compress, the single working stage of the discharge of expansion and spent fuel-air mixture.

Start from article that disclosed rolling piston compressor has four pistons altogether the described document in its housing.These four pistons are separately positioned in the piston retainer in each receiving means, and wherein, the piston retainer centers on the rotating shaft revolution fixing with housing with piston.Two pistons that are provided with face-to-face have a working room respectively towards between each end face of rotating shaft, it medially is provided with respect to rotating shaft.Known rolling piston compressor correspondingly has two working rooms, and they all are positioned in the rotating shaft.

Be in known rolling piston compressor or in rolling piston compressor of the present invention, all rotating shaft to be interpreted as geometrical axis.

The piston of per two pistons formation that has the working room between it is right.The right piston of piston is implemented in the end position (also being known as top dead center (OT)) of the close rotating shaft of piston and away from the mutual reverse to-and-fro motion between the end position (also being known as dead point, bottom (UT)) of rotating shaft around the rotating shaft revolution time.The volume of the working room in the OT position of the right piston of piston between piston is minimum, and the volume of the working room between piston is maximum in the UT position of the right piston of piston.

In order to derive the to-and-fro motion of piston around the rotation motion of rotating shaft from piston, each piston at its back side, be to have the control travelling mechanism on the one side of its working room under dorsad.In addition, the control travelling mechanism of the piston that same piston is right along cam mechanism with the fixing control cam operation of housing, this control cam centers on the rotating shaft extension and has corresponding profile on all faces, derive its to-and-fro motion in order to from piston around the rotation motion of rotating shaft.

Each piston of known rolling piston compressor also is equipped with leads go back to mechanism, gets back to the UT position in order under the situation of higher rotation speed piston led from the OT position.The mechanism that respectively leads back of each piston moves at the control cam adjacent with the control cam that is used for controlling travelling mechanism, and wherein, these two control cams extend substantially in parallel to each other.

The control travelling mechanism of each piston is designed to pulley, its spin axis when piston turns round and rotating shaft form variable section, wherein the spin axis here also can be regarded as geometrical axis.

Shortcoming can appear in rolling piston compressor known under the situation of higher rotation speed, be piston move to from end position not only with its each travelling mechanism touch controls cam away from the process of the end position of rotating shaft near rotating shaft, and, between this piston body segmentation and cam mechanism, produce sliding friction thus with its piston body segmentation contact cam mechanism.Between the receiving means of piston and piston retainer, also produce sliding friction.This sliding friction is big more, and piston is then high more around the rotating speed of the rotation motion of rotating shaft, and this is to compress towards cam mechanism consumingly gradually because of the radial centrifugal force described piston body segmentation before that the rotating speed with raising that acts on the piston increases.

The extra setting of travelling mechanism of piston itself and known rolling piston compressor lead back the sliding friction that mechanism all can not stop the plane of the rising that is caused by centrifugal force.The rotating speed that raises causes known rolling piston compressor power loss and wearing and tearing to increase.

Summary of the invention

Therefore the objective of the invention is to, the rolling piston compressor that article is started described type improves, thereby avoids or reduce at least the power loss that sliding friction caused and the wearing and tearing of the piston that is caused by centrifugal force.

According to the present invention, this purpose in view of article starts described rolling piston compressor so realize, piston also has auxiliary travelling mechanism in the outside side of centrifugal force direction (fliehkraftseitig) except control the travelling mechanism for rotating shaft, its running face when reciprocating motion of the pistons along the inner side surface roll extrusion of piston retainer (

), wherein the moving direction and the rotating shaft of auxiliary travelling mechanism are positioned at same plane.

Therefore in rolling piston compressor according to the present invention, at least one piston not only has the reciprocating control travelling mechanism that piston is derived in the rotation motion that is used for from piston around rotating shaft, also additionally has auxiliary travelling mechanism, it is not the to-and-fro motion that is used for control piston, but the support on piston retainer inner side surface of the roller supporting of the outside side of control centrifugal force direction.In this way, piston is from no longer standing sliding friction near the end position of rotating shaft up to the total movement travel away from the end position of rotating shaft, and only also stands rolling friction.Therefore rolling friction is obvious littler and cause the power loss of rolling piston compressor and wearing and tearing obviously to reduce with respect to planar friction.

Auxiliary travelling mechanism so is arranged on the piston, makes the moving direction of auxiliary travelling mechanism and piston be positioned at common plane around its rotating rotating shaft in housing.Guarantee that thus piston is supported on the piston retainer by auxiliary travelling mechanism towards the outside side of centrifugal force direction all the time.Because the piston retainer around the rotating shaft revolution, does not produce the friction perpendicular to the orbit of auxiliary travelling mechanism with piston between the inner side surface (auxiliary travelling mechanism is in roll extrusion on this inner side surface) of auxiliary travelling mechanism and piston retainer.

Auxiliary travelling mechanism is designed to pulley in preferred design, and its spin axis points to perpendicular to the rotating shaft of the rotation motion of piston.

Auxiliary travelling mechanism also can be with the form design of spherical parts, its can on the back side of piston on all direction in spaces free rotation ground supporting in ball bearing, and the advantage that will assist travelling mechanism to be designed to pulley is, if the spin axis of auxiliary travelling mechanism points to perpendicular to the rotating shaft of the rotation motion of piston, the then auxiliary roll extrusion of travelling mechanism on the inner side surface of piston retainer clearly limits, and, avoided increasing the slide effect of friction as the situation of the spherical parts that does not center on the spin axis rotation that defines.

In another preferably designed, the control travelling mechanism was designed to pulley, and its spin axis is intersecting with rotating shaft on the same point in enclosure interior near the end position of rotating shaft with on away from each position between the end position of rotating shaft at piston.

This measure is the further improvement with respect to known rolling piston compressor.Though the control travelling mechanism is designed to pulley equally in known rolling piston compressor, in the orientation of the spin axis of known rolling piston compressor middle pulley according to piston in close rotating shaft with away from the position change between the end position of rotating shaft.In known rolling piston compressor, the pulley of control travelling mechanism loads by the power that favours its spin axis and point to, and this power exceedingly loads the pulley bearings of pulley and under disadvantageous situation even can be locked.

Avoided adverse influence in the previous designs according to rolling piston compressor of the present invention, the spin axis of its middle pulley is preferably radially pointing to the housing central point at piston near rotating shaft with in away from each position between the end position of rotating shaft.

In another preferably designed, the pulley of auxiliary travelling mechanism was arranged in the bearing in the pulley of control travelling mechanism, wherein, and the mutual vertical setting of spin axis of the pulley of auxiliary travelling mechanism and control travelling mechanism.

The advantage of this measure is the structure in auxiliary travelling mechanism and the special saving space of control travelling mechanism on piston.In addition, the bearing of the pulley of control travelling mechanism correspondingly is designed to hollow body, and it holds the pulley of auxiliary travelling mechanism, and wherein, only the excircle of the pulley of auxiliary travelling mechanism is outstanding, and it is used as along the running face of the inner side surface roll extrusion of piston retainer.

In another preferably designed, the to-and-fro motion of piston was the oscillating motion that centers on perpendicular to the axis of oscillation of rotating shaft, and the running face of control travelling mechanism is oriented on the intersection point of axis of oscillation and rotating shaft in each position of piston with the Line of contact of controlling cam.

In this design on the Normal direction that is positioned at the control cam in each position of running face at piston of advantageously having guaranteed the control travelling mechanism under the situation that plunger designs is become oscillating-piston and avoided the slant operation of auxiliary travelling mechanism thus along the control cam.Therefore produced the perfect parallelism of the traffic direction of control travelling mechanism with respect to the control cam.

In another preferably designs, the piston retainer has from around the narrow of the circumferencial direction of rotating shaft and the elongated convex shoulder that looks up from the side of rotating shaft at the auxiliary travelling mechanism of piston, and this convex shoulder is extending on the direction away from the end position of rotating shaft of the auxiliary travelling mechanism of piston.

Here advantage not only be auxiliary travelling mechanism at it from up to stroke, only contacting all the time with the inner side surface of piston retainer away from the end position of rotating shaft near the end position of rotating shaft, and not with its on design have the cam mechanism of control cam contact, and because narrow and so the structure of limited convex shoulder also worth mentioning for the increase of the weight of piston retainer.

In another preferably designs, on the inner side surface (auxiliary travelling mechanism is along this inner side surface operation) of piston retainer, be designed for the guiding device of the side of auxiliary travelling mechanism.

The advantage of this measure is, can prevent better that piston from tumbling perpendicular to the orbit of auxiliary travelling mechanism, prevents in other words that perhaps piston from tumbling on the gyratory directions of rotating shaft at it.

Other advantage and feature provide from following specification and accompanying drawing.

Obviously, aforesaid and following also not only can be in the combination that each provides with the feature of explanation, and can be in other combination or independent the use, can not depart from the scope of the present invention.

Description of drawings

Show with reference to the accompanying drawings and the detailed description embodiments of the invention.Wherein:

Fig. 1 is the longitudinal section perspective view along the rolling piston compressor on the plane that comprises rotating shaft;

Fig. 2 is the longitudinal section same as in figure 1 with respect to the amplification of the part that relates to piston, piston retainer and cam mechanism of the rolling piston compressor among Fig. 1;

Fig. 3 is and the similar diagrammatic sketch of Fig. 2, wherein, and the not shown piston in the cross section;

Fig. 4 be piston, piston retainer and cam mechanism structural configuration with the similar diagrammatic sketch of Fig. 2, wherein, piston illustrates with another end position with respect to Fig. 2 and 3;

Fig. 5 a) and b) be the single piston of the rolling piston compressor among Fig. 1, wherein, Fig. 5 a) has showed the three-dimensional view of piston and vertical middle section figure that Fig. 5 b has showed piston;

Fig. 6 is the three-dimensional view of piston together with the structural configuration of cam mechanism, and this cam mechanism has the control cam, and wherein, cam mechanism is vertically shown in the middle section;

Fig. 7 is the three-dimensional vertically middle section figure of the cam mechanism under the independent state;

Fig. 8 is the three-dimensional view of the piston retainer under the independent state;

Fig. 9 is vertical middle section figure of the piston retainer among Fig. 8; And

Figure 10 a) and b) be two sectional views that cut down part at the piston retainer in the convex shoulder zone of the piston retainer of the auxiliary travelling mechanism that is used for guiding arbitrary piston, wherein, Figure 10 a) showed do not have a piston cut down part and Figure 10 b) showed the part that cuts down that has piston.

Embodiment

In Fig. 1, showed the rolling piston compressor that has reference character 10 on the whole.Other details of rolling piston compressor 10 is shown in Fig. 2 to 10.

Rolling piston compressor 10 can be designed to internal-combustion engine at large, but also can be designed to pump or compressor under the situation of corresponding modify.

Rolling piston compressor 10 has housing 12, and it has intermediate portion 14 and

end cap

16 and 18 of spherical designs.Housing 12 has the inner chamber 20 of ball symmetric design.

According to Fig. 1 to 3, four

pistons

22,24,26 and 28 are set in housing 12 altogether, wherein, piston 28 is arranged in the place ahead on diagrammatic sketch plane and therefore only at the three-dimensional view of Fig. 3 as seen in the diagrammatic sketch of Fig. 1 and 2.

In rolling piston compressor 10

work piston

22,24,26 and 28 in housing 12 one common peripheral around with fixing rotating shaft 30 revolutions of housing.Rotating shaft 30 is understood that geometrical axis here.Piston 22,24,26 and 28 gyratory directions around rotating shaft 30 illustrate with arrow 32 in Fig. 1.The ball's dead center of the inner chamber 20 of housing 12 is passed in rotating shaft 30.

Rotating shaft 30 is fixing with housing, and this so understands, i.e. the position of rotating shaft 30 remains unchanged during

piston

22,24,26 and 28 revolutions.

In the

piston

22,24,26 and 28, by

piston

22 and 24 form first piston to and to form second piston by

piston

26 and 28 right.For rotating shaft 30, the piston that forms by

piston

26 and 28 to respect to the piston that forms by

piston

22 and 24 to 90 ° around rotating shaft 30 settings of staggering, as especially from Fig. 6 also as seen, wherein showed the three-dimensional views of four structure of piston layouts.

Each piston is to limiting a working room, and promptly

piston

22 and 24 limits working room 34 and

piston

26 and 28 qualification working rooms 36 (referring to Fig. 2).Be not subjected to

piston

22,24,26 and 28 to center on the influence of the rotary position of rotating shaft 30, be understood that working

room

34 and 36 are passed in the rotating shaft 30 of geometrical axis all the time.

Working room 34 is limited by the

end face

38 and 40 towards rotating shaft 30 of piston 22 and 24.Working room 36 is correspondingly by limiting (referring to Fig. 4) towards (the piston 26) end face 42 of rotating shaft 30 and the end face 44 of (piston 28).

In working

room

34 and 36, carry out the single working stage of the discharge of the collision of the mixture of lighting, lighting of compression, mixture of the entering of fuel-air mixture, mixture and the mixture that burnt.

Working room

34 and 36 periodically becomes big and diminishes for this reason, and promptly working

room

34 and 36 becomes big each other in the same way and diminishes in an illustrated embodiment.But the aforesaid single working stage in two

working rooms

34 and 36 differs two stage phase places, promptly such as the working stage that carries out the compression of fuel-air mixture in the working room 34, then carry out the working stage of the discharge of spent fuel-air mixture in the working room 36, the rest may be inferred.

In order to make

working room

34 and 36 become big and to diminish on

piston

22,24 and 28 revolution period ground,

piston

22,24,26 and 28 its center on be implemented in during rotation motion is done in rotating shaft 30 Fig. 1 to 3 pass the imperial examinations at the provincial level the end position of the close rotating shaft shown in the example and such as shown in Figure 4 away from the to-and-fro motion between the end position of rotating shaft.Piston 22,24,26 and 28 the end position according to the close rotating shaft of Fig. 1 to 3 also are known as top dead center (OT) and are known as dead point, bottom (UT) according to the end position away from rotating shaft of Fig. 4.

Piston 22,24,26 and 28 to-and-fro motion are oscillating motion in an illustrated embodiment.Piston 22,24 is implemented the oscillating motion around axis of oscillation 46 around rotating shaft 30 revolution the time, this axis of oscillation roughly vertically intersects with rotating shaft on the ball's dead center of the inner chamber 20 of housing 12.Piston 26 and 28 is correspondingly implemented the oscillating motion around axis of oscillation 48 (referring to Fig. 2), and this axis of oscillation roughly vertically intersects with rotating shaft 30 on the ball's dead center of the inner chamber 20 of housing 12 and extends perpendicular to axis of oscillation 46 in addition.

In description control mechanism (utilizing this control mechanism to center on the to-and-fro motion of deriving

piston

22,24,26 and 28 rotation motion of rotating shaft 30) before from

piston

22,24,26 and 28, at first describe piston retainer 50 (Fig. 8) in detail, in the piston retainer, hold

piston

22,24,26 and 28 with reference to Fig. 2 to 4 and 8 and 9.Piston retainer 50 is a rotor, and it turns round around rotating shaft 30 with

piston

22,24,26 and 28.For rotating shaft 30,

piston

22,24,26 is connected with piston retainer 50 is correspondingly antitorque with 28, but can implement its oscillating motion with respect to the piston retainer.

According to Fig. 8 and 9, piston retainer 50 is being engaged by two and

half parts

52 and 54 on the direction of rotating shaft 30, and this two and half part removably interconnects along closing line 56, is mutually permanently connected by means of bolt such as

half part

52 and 54 of piston retainer 50.According to Fig. 4, half part 52 of piston retainer 50 has hole 58 cylindrical or arc-shaped bend slightly and is used to hold piston 22 and 24.Piston 22 and 24 is implemented reverse each other to-and-fro motion in hole 58, and wherein,

piston

22 and 24 rounded basically on cross section is introduced in the hole 58 slidably.Correspondingly form the boundary on the circumference of working room 34 in the wall portion in the hole 58 between the

end face

38 and 40 of piston 22 and 24.Because

piston

22 and 24 implements oscillating motion in hole 58,

piston

22 and 24 be not be designed to cylindrical, but elbow-shaped.

According to Fig. 2, design has cylindrical hole 60 in the second half parts 54 of piston retainer 50, holds

piston

26 and 28 in this hole.The cylindrical hole 58 of

piston retainer

50 and 60 structural configuration corresponding to

aforesaid piston

22,24,26 and 28 stagger with 90 ° mutually with respect to rotating shaft 30.Piston 26 and 28 also is designed to have the syphon shape of circular cross section as piston 22 and 24.But equally also can consider other cross section (such as elliposoidal).

According to Fig. 1, piston retainer 50 can be bearing in the housing 12 rotatably around rotating shaft 30.

Beginning description control mechanism utilizes this control mechanism to derive the to-and-fro motion of these pistons from

piston

22,24,26 and 28 rotation motions that center on rotating shaft 30 below.

For this reason, according to Fig. 1, in housing 12, control cam 62 is set regularly with housing.Here with the fixing expression of housing, control cam 62 itself does not participate in the rotation around rotating shaft 30, but the notion of " fixing with housing " also comprises this situation, promptly control cam 62 and can carry out position regulation, such as, in order to stroke in regulating

piston

22,24,26 near the end position of rotating shaft and between and 28 away from the end position of rotating shaft.

In Fig. 7, showed at vertical middle section perspective view perpendicular to the control cam 62 in the plane of rotating shaft 30.Control cam 62 has the installing ring 64 that designs around rotating shaft 30 on all faces, will control cam 62 by this installing ring and be installed in the housing 12.Cam mechanism 62 has (preferred integratedly be shaped) and sets to the control cam 66 of

piston

22 and 24 and set control cam 68 (referring to Fig. 2 and 4) to

piston

26 and 28 on installing ring 64.

Control cam

66 and 68 centers on rotating shaft 30 extensions equally and has band with respect to the crest of rotating shaft 30 and the profile of trough on all faces, in order to center on the to-and-fro motion of deriving these pistons the rotation motion of rotating shaft 30 from

piston

22,24,26 and 28.

Control in addition that

cam

66 and 68 ball's dead centers with respect to the inner chamber 20 of housing 12 are symmetrical arranged and therefore basic quadrature in rotating shaft 30.

Each

piston

22,24,26 and 28 all has the control travelling mechanism, and it moves along

control cam

66 or 68 when each

piston

22,24,26 and 28 turns round around rotating shaft 30.

Such as in Fig. 2 as seen, piston 22 has control travelling mechanism 70 and piston 24 and has control travelling mechanism 72, and has control travelling mechanism 74 and piston 28 has control travelling mechanism 76 according to Fig. 4 piston 26.

The design of

control travelling mechanism

70,72,74,76 is mutually the same, therefore only describes the design of the control travelling mechanism 70 of piston 22 below.

Fig. 5 a) and b) in showed piston 22 with independent state, simultaneously also will be referring to Fig. 2.

Control travelling mechanism 70 is designed to pulley 78, and it is rotatably mounted around spin axis 80.In addition, pulley 78 is bearing in respect on the antitorque bearing cage 82 of spin axis 80 and therefore be connected with piston 22.Control travelling mechanism 70 on piston 22 is positioned at the back side back on end face 38, this end face under the mounted state of piston 22 towards the working room 34.Pulley 78 has running face 84, and it extends along the control cam 66 of control mechanism 62 according to Fig. 2.Running face 84 along when operation pulley 78 around spin axis 80 rotations.As can be seen from Fig. 2, spin axis 80 is radially aimed at respect to the ball's dead center of the inner chamber 20 of housing 12, and particularly aims in other words and intersect with this swing axis to swing axis 46 (piston 22 is around this swing axis swing).Spin axis 80 is not intersected with rotating shaft 30 on the same point of rotating shaft 30 all the time about the influence of the position of swing axis 46 by piston 22.

Running face 84 be taper and so aim in addition, make the running face 84 of pulley 78 on any position of piston, all aim at the intersection point of axis of oscillation 46 and rotating shaft 30, promptly aim at the ball's dead center of the inner chamber 20 of housing 12 with the Line of contact 86 (Fig. 2) of control cam 66.Guaranteed thus between pulley 78 and control cam 66, slant operation can not occur, thereby also do not had tilting force to act on the pulley 78.

But

piston

22,24,26 and 28 not only has a control travelling mechanism (its function is to center on the to-and-fro motion of deriving these pistons the rotation motion of rotating shaft from

piston

22,24,26 and 28) respectively, except each control travelling mechanism, also have an auxiliary travelling mechanism, will be described in greater detail hereinafter.

Have auxiliary travelling mechanism 88 and piston 24 has auxiliary travelling mechanism 90 according to Fig. 2 piston 22, and have auxiliary travelling mechanism 92 and piston 28 has auxiliary travelling mechanism 94 according to Fig. 4 piston 26.

Owing to assist travelling

mechanism

88,90,92 and 94 mutually the same designs, therefore only describe the auxiliary travelling mechanism 88 of pistons 22 below in detail with reference to Fig. 2 and 5.Auxiliary travelling mechanism 88 is designed to pulley 96, and its spin axis 98, but does not intersect with it perpendicular to rotating shaft 30 orientations according to Fig. 2.In addition, spin axis 98 is perpendicular to spin axis 80 orientations of the pulley 78 of control travelling mechanism 70.In addition, the pulley 96 of auxiliary travelling mechanism 88 such as by needle roller bearing support in the bearing cage 82 of the pulley 78 of control travelling mechanism 70.

The auxiliary travelling

mechanism

92,92 of auxiliary travelling mechanism 88 and

other piston

24,26 and 28 and 94 wherein, is supported on the inner side surface of piston retainer 50 as at outside side support piston 22 of centrifugal force direction and

piston

24,26 and 28.

According to Fig. 8 and 9, on piston retainer 50, set convex shoulder 100 (being used for auxiliary travelling mechanism 88), 102 (being used for auxiliary travelling mechanism 90) and 106 (being used for auxiliary travelling mechanism 94) of roof shape for each auxiliary travelling

mechanism

88,90,92 and 94.Be used for auxiliary travelling mechanism 92 corresponding roof shape convex shoulder 104 at Fig. 4 as seen.Convex shoulder 100,102,104 and 106 is from being designed to narrow and being seen as elongated from the direction of rotating shaft 30 around the circumferencial direction of rotating shaft 30, wherein, convex shoulder 100,102,104 and 106 is extending on the direction away from the end position of rotating shaft of each

piston

22,24,26 and 28.In Fig. 4 special exhibition be used for the convex shoulder 104 of auxiliary travelling mechanism 92 of piston 26 and the convex shoulder 106 that is used for the auxiliary travelling mechanism 94 of piston 28 accordingly.Fig. 4 has showed and has been arranged in its

piston

26 and 28 away from the end position of rotating shaft that working room 36 has maximum volume in this position.

In addition, auxiliary travelling

mechanism

88,90,92 and 94 roll extrusion on the inner side surface of each convex shoulder 100,102,104 and 106, wherein, thus its reciprocal traffic direction and the rotating shaft 30 in other words of the auxiliary travelling

mechanism

88,90,92 of each of Miao Shuing and 94 orbit be arranged in common parallel, such as from Fig. 2 and Fig. 4 as seen.In Fig. 2, assist the current moving direction of travelling

mechanism

88 and 90 to be arranged in the diagrammatic sketch plane, in Fig. 4, assist the moving direction of travelling

mechanism

92 and 94 to be arranged in the diagrammatic sketch plane.Because

piston

22,24,26 is connected with piston retainer 50 with 28 antitorquely, assist travelling

mechanism

88,90,92 and 94 only to be implemented in the roll extrusion campaign that is parallel to rotating shaft 30 on the piston retainer 50 with respect to piston retainer 50.

Because

piston

22,24,26 is connected with respect to rotating shaft 30 with piston retainer 50 with 28, has guaranteed to prevent tumbling with respect to rotating shaft 30 thus antitorquely.In order further to improve anti-tipping stability, the guiding device of the big tubbiness of design side on the inner side surface of the convex shoulder 100,102,104 of roof shape and 106, each auxiliary travelling

mechanism

88,90,92 and 94 is supported on this guiding device laterally.Figure 10 a) and b) in showed convex shoulder 100 and the auxiliary travelling mechanism 88 that is used for the roof shape, the running face 108 of auxiliary travelling mechanism 88 is roll extrusion and

projection

112 and 114 guiding by corresponding big tubbiness laterally on the inner side surface of convex shoulder 100.

Auxiliary travelling

mechanism

88,90,92 and 94 with the corresponding convex shoulder 100,102,104 and 106 of piston retainer 50 avoided to a

great extent piston

22,24,26 and 28 the friction on the piston retainer 50 and avoided with the fixing parts of housing on sliding friction, this friction meeting occurs in known rolling piston compressor.In known rolling piston compressor, be reduced in the obviously littler rolling friction by auxiliary travelling

mechanism

88,90,92 and 94 in this sliding friction on the piston retainer 50.

With reference to Fig. 1, rolling piston compressor 10 is being designed to also have a light up

plug

115 and 116 respectively at each working

room

34 and 36 under the situation of internal-combustion engine, and they guide by

end cap

16 and 18 at end face respectively.The exhaust branch pipe 120 that working room 34 also is equipped with the air intake branch 118 that is used for combustion air and is used to discharge spent fuel-air mixture.At working room 36 corresponding structure is set also.

Piston

22,24,26 and 28 is passed on the working shaft 122 together with the rotation motion of piston retainer 50 around rotating shaft 30, and this working shaft rotatablely moves such as being used to drive truck then.

Claims

1. rolling piston compressor, has housing (12), at least one first piston (22) is set in housing, described first piston can center on rotating shaft (30) revolution fixing with housing, and between near the end position of rotating shaft and end position, implementing to-and-fro motion away from rotating shaft around rotating shaft (30) when revolution, with so that go up the working room (34) that limits at the end face towards rotating shaft (30) (38) of piston (22) and periodically become greatly and diminish, wherein, rotating shaft (30) is passed working room (34) and is extended, piston (22) has control travelling mechanism (70), edge and fixing control cam (66) operation of housing when it turns round around rotating shaft (30) at piston (22), in order to from rotation motion, to derive the to-and-fro motion of piston (22), and piston (22) is arranged in the receiving means of piston retainer (50), piston (22) connect with respect to rotating shaft (30) with the piston retainer antitorquely and piston retainer and piston (22) around rotating shaft (30) revolution, it is characterized in that, piston (22) also has auxiliary travelling mechanism (88) with respect to rotating shaft (30) in the outside side of centrifugal force direction except having control travelling mechanism (70), the running face (108) of auxiliary travelling mechanism in the to-and-fro motion of piston (22) along the inner side surface roll extrusion of piston retainer (50), wherein, the moving direction and the rotating shaft (30) of auxiliary travelling mechanism (88) are arranged in common plane.

2. according to the described rolling piston compressor of claim 1, it is characterized in that auxiliary travelling mechanism (88) is designed to pulley (96), the spin axis of described pulley (98) is perpendicular to rotating shaft (30) orientation of the rotation motion of piston (22).

3. according to claim 1 or 2 described rolling piston compressors, it is characterized in that, control travelling mechanism (70) is designed to pulley (78), and the spin axis of described pulley (80) is crossing in same point housing (12) near the end position of rotating shaft and on away from any position between the end position of rotating shaft and rotating shaft (30) at piston (22).

4. according to claim 2 and 3 described rolling piston compressors, it is characterized in that, the pulley (96) of auxiliary travelling mechanism (88) is arranged in the bearing in the pulley (78) of control travelling mechanism (70), wherein, the spin axis (98,80) of the auxiliary travelling mechanism (88) and the pulley (96,78) of control travelling mechanism (70) is vertical mutually.

5. according to each described rolling piston compressor in the claim 1 to 4, it is characterized in that, the to-and-fro motion of piston (22) is around the oscillating motion perpendicular to the axis of oscillation (46) of rotating shaft (30), and the running face (84) of controlling travelling mechanism (70) in any position of piston (22) is aimed at the intersection point of axis of oscillation (46) and rotating shaft (30) with the Line of contact (86) of control cam (66).

6. according to each described rolling piston compressor in the claim 1 to 5, it is characterized in that, piston retainer (50) has the elongated convex shoulder of seeing on the circumferencial direction of rotating shaft (30) (100) narrow and that look up in the side of rotating shaft at the auxiliary travelling mechanism (88) of piston (22), and described convex shoulder extends and assists travelling mechanism (88) to move on the inner side surface of convex shoulder towards the end position away from rotating shaft of piston (22).

7. according to each described rolling piston compressor in the claim 1 to 6, it is characterized in that, be designed for the guiding device of the side of auxiliary travelling mechanism on the inner side surface of piston retainer (50), wherein, auxiliary travelling mechanism (88) moves along described inner side surface.