DE1453675C3 - Device for pressing the cylinder drum of an axial piston machine against the control plate - Google Patents

Description

3 4

F i g. 3 a schematic view of the hydraulic outlet pressure optionally in the passages or lines

The circuit of one of the inventions 31, 32 running as a pump becomes effective. The passage or the

axial piston machine according to the invention, line 31 is connected to one of the passages 20 or 21

F i g. 4 is a partial sectional view of an inventive axial piston machine 10 connected, while the

moderate axial piston machine, S line 32 with the other of the two passages

F i g. 5 is a plan view of the control plate. In this way, the axial piston

Long the line 8-8 in Fig. 4, benmotor 10 depending on the position of the control of the

F i g. 6 shows a plan view of a modified four-way valve 30 in different directions of rotation

management form of the control plate and operated.

F i g. 7 shows a plan view of the one located opposite the control plate inside the drive pulley chamber 25 Side of the steering mirror plate. sensitive pressure medium is indicated in the following

In Fig. 4 are the essential components of the manner described on an between outlet and axial piston machine 10 according to the invention is maintained inlet pressure lying value. For this is how represents that a housing 11 and a rotatable in F i g. 1 is shown, a pressure adjustment valve 35 can be placed Has cylinder drum 12, seen in a 15, the lines 36 and 37 with the Number of cylinders 13 are provided in which passages 31 and 32 are connected. This pressure piston 14 are arranged to be movable back and forth. adjusting valve sets the in the drive pulley space 25 Piston rods 15 are at one end with the prevailing pressure of about the arithmetic Miteinem Universal joint on the piston 14 and at their tel of the outlet and inlet pressures, d. H. of pressures the other end via a universal joint 17 with the ao in the passages 31 and 32. For this purpose is the Drive pulley 16 connected. The drive pulley 16 is drive pulley space 25 via a line 38 with the connected to the drive shaft (pump) or output shaft valve 35.

(Motor) connected. Between the drive shaft and the pressure adjustment valve 35 can be of any geder The cylinder drum is a double cardan joint of a suitable design, with which the specified pressure is provided, so that the drive force between the drive value setting is possible. Preferably will shaft and cylinder drum also with angular position that in F i g. 2 is used, in which in transmits from their axes of rotation. a housing 40, which is also from the housing of the axial

The cylinder drum 12 is located on which the control piston machine itself can be formed, in

Mirror-forming underside of a control mirror plate diameter of valve chambers of different sizes

19, the two passages 20 and 21 (Fig. 5) are formed on 30 43, 44, to which channels 41 and 42 instructs, which are closed off when the cylinder drum rotates, which are connected to lines 36 and 37 are alternately with the ends of the cylinder 13 in connection. In the valve chambers 43, 44 bond come. When the axial piston machine 10, a stepped piston 45 is used, its in the Durchais Pump is operated, d. that is, when the drive knife has a smaller portion 46 in the valve chamber 43 shaft is driven, slides to one of the passages 35, while the larger diameter piston 20, 21 a connection to a pressure medium supply part 47 in the chamber 44 is displaceable. The about produced, while the other passage with the pressure transmitted through the channel 41 acts on the forehead Pressure medium to be supplied to the device connected-side surface 50 of the valve piston part 46, while that will. When the drive shaft is driven, the pressure supplied via channel 42 oscillates on the the pistons 14 in the revolving cylinder drum 40 annular surface 49 at the end of the piston part 47 larger 12, and acts through the diameter passage forming the inlet. The surface 49 behaves

20 pressure medium is sucked in, which through the to the surface 50 and to the surface 51 at the free end of the Outlet-forming passage 21 is displaced. Is piston part 47 of larger diameter so that the the axial piston machine 10 operated as a motor, the outlet pressure from the outlet channel 52 equal to that becomes one of the passages 20 or 21 under pressure 45 arithmetic mean of the pressures in the channels 41 standing pressure medium supplied, which is through the and 42 is. The outlet channel 52 is on the line whose passage exits again, with the piston 14 38 connected. This is achieved in that are driven, which in turn, the drive pulley 16, the area 49 is dimensioned equal to the area 50, and rotate the output shaft. The direction of rotation of the each of these surfaces, in turn, half the surface-axial piston motor depends on which of the 50 surface area 51 has. Self-regulating pressure outlets 20 or 21 the pressure medium supplied adjusting valves of this type are known per se. As will. The configuration described so far can, however, also include other valve types Axial piston machine can also be used with known Ma-

machines realized. Since the cylinder drum 12 by the on their at-Die Drive pulley chamber 25 is loaded with pressure medium within the housing 11, which is essentially closed to pressures acting on the sides. its pressure preferably on one of the voltage expediently, which the cylinder drum arithmetic mean of inlet and outlet pressure 12 in contact with the control plate 19 holds. To do this, corresponding value is maintained. as usual in axial piston machines, a spring

Like F i g. 1 shows, the Axial 60 will be turned during operation.

piston machine as a motor pressure medium via a line. In Fig. 5, an additional possibility is shown.

device L _{1 is} supplied to a four-way servo valve 30 and sets, with which the cylinder drum 12 on the control

returned via a line L ₂ . The four-way mirror can be kept by applying a low pressure

Servo valve has two passages, which are optionally in pockets 57 and 58 in the control plate 19 on the

with the inlet line L ₁ and the outlet line L ₂ 65 cylinder drum 12 is brought into action,

can be connected by the fact that the control system creates a sufficient pressure asymmetry

element of the valve, for example a piston slide, which the cylinder drum 12 on

About, is set so that the inlet pressure and the control plate 19 holds in contact. As shown in FIG. 1 her-

happens, this is achieved via lines 55 and 56, which are connected to lines 31 and 32 and via a line 59 to the pockets 57 and 58 in connection. Check valves 60 and 61 are provided in lines 55 and 56 so that only low pressure prevails in pockets 57 and 58 , while the respective check valve closes when high pressure is applied. The pockets 57 and 58 serve to form areas of lower pressure, through which the high system pressure acting on the cylinder block 12 is compensated.

If the in Fig. 1 is put into operation by switching on the four-way valve 30 , the drive pulley space 25 (FIG. 4) is subjected to a pressure corresponding to the arithmetic mean of the inlet and outlet pressures. This compensates for the forces acting on the cylinder drum 12 , whereby the bearing forces are also reduced, so that the bearings used can be dimensioned weaker and a more compact machine design is possible.

Since the same pressures prevail in the passages 20 and 21 of the motor in the neutral position of the four-way valve, and since the pressure load on the housing is equal to the arithmetic mean of the sum of the two pressures, the effort required to operate the motor with a small switching movement is increased of the servo valve in one direction or the other in Betueb is significantly reduced. This can be seen clearly from Table I below.

Table I. Weight (dry) .. test Engine with Hand torque More conventional Pressure compensation with 0 kg / cm ² engine 0.771 kg both openings 0.907 kg Hand torque at 105 kg / cm ² 0.829 cmkg both openings 0.576 cmkg Breakaway pressure difference (in the clock 1,440 cmkg clockwise) 10.368 cmkg operating pressure difference (in the clock 5.11 kg / cm * clockwise) 37.80 kg / cm ² Breakaway pressure -difference (in Ge 3.08 kg / cm ² counter-clockwise) ... 26.04 kg / cm ² operating pressure difference (in Ge 4.90 kg / cm ² counter-clockwise) ... 39.20 kg / cm ² Tightening torque Maximum value 2.94 kg / cm ² Minimum value 25.41 kg / cm ² Average 49.3056 cmkg 48.1536 cmkg 47.6928 cmkg 45.8496 cmkg 48.32640 cmkg 46.73664 cmkg

From the table above it can be seen that not only those to break loose, i. H. Start off the standstill, required difference is significantly reduced, but that the axial piston machine when working as a motor also has a higher tightening torque than the axial piston machine hf Licher design with comparable Konstruktk In addition, it was found that German in the described servo valve operation over the th pressure difference range from 24.5 to 21 between high and low pressure side an efficiency and an increased effective moment has. If the Axialkc machine is operated as a pump, the four-way valve is not required

ίο the circuit shown in Figure 3 is used v pumps usually only in one direction ε ben, only one line 56 is from while the circuit is otherwise essentially F i g. 1 corresponds to the circuit shown.

Even when operating the Axialkolbenmasch pump according to FIG. 3 are the compensation outlined advantages including increase in efficiency through Vermin the leakage losses achieved. Also for pump bed

so therefore a reduction in ur bearing load more compact and weight-saving construction borrowed.

In the Fi g. 6 and 7 is a modified form of the one marked 122 , the Stet:

as gel 121 carrying control mirror plate gezeig control the mirror plate 122 has kidney-shaped I and outlet passages 136 and 137 are the m inlet and outlet of the machine housing ii binding to the admittance or Austri to enable printing means. By a D:

the control mirror plate 122 can have a phase curve:

between the cylinder drum and the mirror plate can be achieved.

As in Fig. 6 is shown, which is provided with a Steuerspiege lying in the vicinity of the inlet Let arcuate pocket 138 in Steue gel 122 and 121 also includes an arcuate T 139 in the control mirror 121 to the outlet passage in the 137th A channel 14C connects the bore 141 T 138 to the outlet passage 137, the Bo _:

141 sets the control plate plate from the bottom of the T 138 to the opposite surface 142 d. From the rear of the bore 141 of the surface 142 performs a communicating groove 143 for laßdurchlaß 137, whereby the compound de: see 138 to outlet passage we made is Similarly, the pocket passage 139 with the egg 136 is connected by a duct provided with a bore 144th The bore in turn extends from the bottom of the pocket to the opposite surface 142 of the control plate 122. A connecting groove 146 in the F

142 then re-establishes the connection to the egg passage 136 .

Since the pressures in the pockets 138 and 139 prevail in each case just the one in the neighboring. Inlet and outlet passages 136, 137 Reign the pressures are opposite to resulting force gives to the Zylindert: mel such that an attempt to counteract the high pressure side abzukippen control mirror, additionally this effect may even by the on voltage of short radially extending pockets and 148 near the ends of the pocket by corresponding pockets 149 and 150 near the ends of the pocket 139

1 sheet of drawings

Claims (4)

Pressures generated by preload pumps in the order of magnitude of 10 kp / cm2 occur. In addition to the 1st device for hydraulic pressure leakage losses 1. Device for hydraulic pressing Lectveriust "ίΑ" "£ SÄT the rotating cylinder drum of an axial 5 and the cylinder bore! ι on dfe SSS piston machine at the front side of which the pressure increases linearly. So fet zwanSfiä Control mirror with a deterioration in the active unity from the high pressure side, Γγ δ> ^g Connection of the machine with pressurization kolbenhi bi iSTt ^ i ^ pg m on the high-pressure side a deterioration of the active unity, Γγ δ> Connection of the machine with pressurized piston machine «at amimSTt ^ i ^ barable pressure chamber, connected thereby. «Nmenaem system pressure net that as a pressure chamber in machines with fluid io The invention is closer to η; » α * κ The leakproof housing is based on the drive pulley space, an AallSlÄSder eLanS (2S) dt d dß i it d Alß (21) d SiA ^ g se is based on the pulley room, an AallSlÄSder eLanS (2S) is used and that one with the outlet (21) and imagined to develop further so that SiA ^ the inlet (20) of the machine (10) in connection see control plate and ZyHn'dertroZ? f ^ " dung standing, known pressure setting between the piston and zSde? hTn valve (35) is provided, which _{controls the pressure in the t 5} tendency leakage flow Tb7 alfenSA Set the nebula space (25) to a value, machine can be reduced so that inS 5? ■ which lies between the inlet and outlet pressure. high hodbaiuLüti ^^^ S ^ Si ^. 2. Device according to claim 1, characterized can be bought degree improvements achieved ^FkUngS indicates that the cylinder drum (12 and this object is erfindunewmäR w 112) solves in a known manner under the bias ao that as a pressure space at Μ? Ε £ ΐ one weak one, it in the direction of the controllability-tight housing of the TrXSLT mirror (19) pressing compression spring stands. and that one with the Ausllß and theEmTaGS 3. Device according to one of claims 1 machine related per selSL or 2 characterized in that the control tes pressure adjustment valve provided ^ t Sas the η J mirror (19) in a known manner with Nie- a ₅ in the drive pulley space on one "Adjust the value of the pressure pockets (57, 58). Between the inlet and outlet pressure 1 in the sense. Dami 4 Device according to one of claims 1, the ZvSertrZ is pressurized to 3, characterized in that the control unit on its control plate Jcenüher ¥ _P £ H Mirror (19) in a known manner with pockets on the front side, the height being def DnS, aLI ⁸ · ^{en (1} ? '"J ³ V Γν. ⁸ ^ ^iSt ' ^the " * ^{sources of sub} - ^{30ness from the} - ™ ^d inlaL ä T ^ different high fluid pressure in connection with even higher accuracy ^{dUng stand} f ^d * the streams of oil f jie Lecl streams z ^ ntn ^ oTbn! is and cylinder bores substantially reduced because the for the Great of leakage veranfwortlSe 35 pressure drop in all operating states of the _ma chine substantially reduced I Atlt d Efi Tv c_c a !. · <* · Machine is significantly reduced The invention relates to a device for hy- In an embodiment of the invention is voroe ^ h ^ n α η hydraulic pressing of the rotating cylinder- the cylinder drum in known? w22 t S der drum of an axial piston machine on whose current preload a weak you; Γ % ■ bdc Front side control plate with a compression spring '™ ^s ™ pushing from the 4 ° control plate Pressure-side connection of the machine with pressure. Pressure spring? but only serves d ™ to the 7vl? η ^ openable pressure space. _me l on the control panel in Tnla _R e _ζ ί haiS, '^ " To reduce the internal leakage losses in not yet a sufficiently high? _D Lk Z 'Ϊ, Γ ** Axial piston machines it is known (German Palischen Anpressung im Triebscheihl ^h y ^out - publication 1003 040) with which 45 is generated on the high pressure side. The spring klnn date ^ im Ge ZTT 'T' system pressure generated a pressure chamber to be pressurized for the largest part of the known M ₁ Si _n ? ^TO , beat that are measured relatively between the cylinder drum and weak ^{Ma schmen} a stationary component of the machine formed A further reduction in τ, ν ι is so that the cylinder drum can see the control plate of the front side Je ^^ Zvlindestm ^, "^ T ' is pressed. This will cause a lifting of the 5 »control mirror can thereby m / ^{And dem} Cylinder drum from the control mirror on the high control chain KS ^ A ^ pressure side and a resulting leak pressure pocket is equipped Enlargement of the gap between the cylinder drum and the alternative or eemeins-im _m > -i counteracted the control level, so that the control level can a ^ ch on this measure We.se between the cylinder drum end face ₅₅ with pockets manner ausgesSt Λ: ^r and the leakage current sources occurring in the control mirror underclScn? ^^^^^ pressure-dependent _{lg is} controlled. Be t f ^ "current" not interrupted because - quite allowed this, connection stand where LS "^ the mutually sliding components serving leakage side a pocket wShenfrt Sl m ^au same low also for heat dissipation and lubrication SystenSucT exposed ςΓ ^{£" 8} ^ V? otherwise a Fres- 6o is applied pressure, and umäkehr ^{system high} sen between the end face of the cylinder barrel and below is a AUSS ί ·. the control plate can not be avoided. invention to Haml the 7eict ^ ™ v "Ssbeispiel the Er in the known Machine is the pressure in the ™ ^? ^ 3SaÄ! ⁸ ? ^I f ⁱ S ^r ? !! ^UterLE " ^zci 8 ^t pressure space thus equal to the high-pressure side pressure dungsiernahrung as engine _en ^" of the system. Some, though lesser 6 _S maschin ™ used has axial piston influence on the lifting of the drum by the control Fig 2 'has Schnittnnsirht u ι ■ mirror, however, the generated on the low pressure side de embodiment "to Snfl." T g ^{Favor te} Pressure, especially since today the DSeSuiSitül 'Druckeinstellun 8 ^{is also used on the low pressure side.}